GB2525277A

GB2525277A - Vibration-reducing structure for compressing diaphragm pump

Info

Publication number: GB2525277A
Application number: GB1500334.6A
Authority: GB
Inventors: Ying Lin Cai; Chao Fou Hsu
Original assignee: Individual
Current assignee: Individual
Priority date: 2014-01-16
Filing date: 2015-01-09
Publication date: 2015-10-21
Anticipated expiration: 2035-01-09
Also published as: CN104791227B; JP6011891B2; DE102015000209A1; CN204591643U; KR20170020826A; KR20150085778A; CN104791227A; KR101835177B1; IN2014MU04211A; GB201500334D0; CN104791226A; JP2015135114A; GB2525277B

Abstract

A compressing diaphragm pump features a pump head body 60 and a diaphragm membrane 70. The pump head body includes, preferably three, operating holes and a first curved vibration-reducing positioning structure 65 circumferentially disposed around the upper side of each operating hole. The diaphragm membrane includes, preferably three, equivalent piston acting zones and second curved vibration-reducing position structures 77 situated at positions corresponding to the positions of the first curved vibration-reducing positioning structures. The first positioning structures in the pump head body, which may be grooves, slots, perforations, or protrusions, mate with the corresponding second positioning structures in the diaphragm membrane, which may be protrusions, grooves, slots, or perforations, to reduce the moment arm L2 generated during pumping by movement of the diaphragm membrane, thereby generating less torque to decrease the strength of vibrations and vibration noise.

Description

Vibration-reducing structure for compressing diaphragm pump

Field Of The Present Invention

The present invention relates to a vibration-reducing structure for compressing a diaphragm pump used in an RU (reverse osmosis) purification system, and particularly to a structure that can reduce the vibration strength of the pump so that the annoying noise incurred by consonant vibration with the housing of the RU purification system is eliminated when the structure is installed on the housing of the RU purification system.

tO Background Of The Invention

Conventional compressing diaphragm pumps, which have been exclusively used with the RU (Reverse Usmosis) purifier or RU water purification system, are disclosed in US. Patent Nos, 4396357, 4610605, 5476367, 5571000, 5615597, 5626464, 5649812, 5706715, 5791882, 5816133, 6048183, 6089838, 6299414, 6604909, 6840745 and tS 6892624. The conventional compressing diaphragm pump, as shown in FIGS. 1 through 9, essentially comprises a brushed or brushless motor 10 with an output shaft 11, a motor upper chassis 30, a wobble plate 40 with an integral protruding cam-lobed shaft, 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 ii 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.

S The eccentric roundel mount 50 includes a central bearing Si at the bottom thereof for receiving the corresponding integral protmding cm-lobed shaft of the wobble plate 40, three eccentric roundels 52 disposed evenly and circumferentially thereon. Each eccentric roundel 52 has a screw-threaded bore 54 and an annular positioning groove 55 formed on a horizontally flush top face 53 thereof The pump head body 60, covers the upper annular rib ring 32 of the motor upper chassis 30 to encompass the wobble plate 40 with integral protruding cam-lobed shaft 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 eccentric roundel 52 in the eccentric roundel mount 50 for receiving each corresponding 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 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 respective radial raised partition ribs 73 connect with the sealing raised rim 71. The diaphragm membrane 70 also includes three equivalent piston acting zones 74 formed 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 respective screw-threaded bores 54 of the eccenific 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. 7 and 8); The pumping pistons 80 are respectively disposed in each of the corresponding piston acting zones 74 of the diaphragm membrane 70. Each pumping piston 80 has a tiered hole St extending therethrough, After the annular positioning protrusions 76 in the diaphragm membrane 70 are inserted into corresponding annular positioning grooves 55 in the 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 74 of each corresponding piston acting zone 74 in the diaphragm membrane 70, so that the diaphragm membrane 70 and three pumping pistons 80 can he securely screwed into screw-threaded bores 54 of the corresponding three eccentric roundels 52 in the eccentric roundel mount 50 (as can be seen in the enlarged view shown in FIG. 9).

Said piston valvular assembly 90, which suitably covers on the diaphragm membrane 70, includes a downwardly extending raised rim 9t for insertion between the outer raised rim 7t and inner raised rim 72 in the diaphragm membrane 70, a central 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 which 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, wherein 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 water-pressurizing chamber 26 is formed in each inlet mount 96 and corresponding piston acting zone 74 in the diaphragm membrane 70 upon insertion of the downwardly-extending raised rim 91 between the outer raised rim 71 and inner raised rim 72 in the diaphragm membrane 70 such that one end of each preliminary water-pressuring chamber 26 is in communication with each of the corresponding inlet ports 97 (as enlarged view shown in FIG. 9 of association); and The pump head cover 20, which covers 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 view of FIG. 9), A high-pressure water chamber 27 is configured 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 by means of pressing the bottom of the annular rib ring 25 on the rim of the central outlet mount 92 (as shown in FIG. 9).

By running each fastening bolt 2 through each corresponding fastening bores 23 of pump head cover 20 and each 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 and pump head body 60 to the motor upper chassis 30 via each corresponding fastening bore 33 in the motor upper chassis 30, the whole assembly of the conventional compressing diaphragm pump is finished (as shown in FIGS. 1 and 9).

FIGS. 10 arid 11 are illustrative figures showing the practical operation mode of the conventional compressing diaphragm pump of FIGS 1-9.

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 eccentric roundels 52 on the eccentric roundel mount 50 sequentially and constantly move in an up-and-down reciprocal stroke, Secondly, the three pumping pistons 80 and three piston acting zones 74 in the diaphragm membrane 70 are in the meantime sequentially driven by the up-and-down reciprocal stroke of the three eccentric roundels 52 to move in an up-and-down displacement.

Thirdly, when the 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-pressurizing 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. 10).

Fourthly, when the eccentric roundel 52 moves in an up stroke causing pumping piston 80 and piston acting zone 74 to be displaced downwardly, 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-pressurizing chamber 26 and increase the water pressure therein up to a range of 8opsi-lOOpsi. The resulting pressurized water Wp causes the plastic anti-backfiow 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 preliminaiy water-pressurizing chamber 26 is directed into high-pressure water 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 shown in FIG. 11 and indicated by arrowhead WP).

Finally, orderly iterative action for each group of outlet ports 95 for the three sectors in central oudet 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 itO-cartridge so that the final filtered pressurized water Wp can be used in an reverse osmosis water purification system.

Referring to FIGS. 12 through 14, a serious drawback caused by vibrations has long existed in the above-described 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 eccentric roundels 52 on the eccentric roundel mount 50 constantly and sequentially move in up-and-down reciprocal stroke, and 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 eccentric roundels 52 to move in 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 HG. 13). Thereby, a resultant torque is created by the acting force F, multiplying the length of moment arm Li as shown by 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 t1 in the motor 10 up to a range of 700-1200 rpm, the S vibrating strength caused by alternate acting of the three eccentric roundels 52 can reach a persistently unacceptable condition To address the direct vibration of the conventional compressing diaphragm pump, as shown in FIG. 14, a cushion base 100 with a pair of wing plates 101 is always provided as a supplemental support. Each wing plate 101 is further sleeved by a rubber shock tO absorber 102 for vibration suppressing enhancement, 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 using the foregoing cushion base 100 with wing plates lOt and rubber shock absorber 102 only addresses the primary direct vibration, while reducing overall vibration only to a limited degree because the primary direct vibration causes a secondary vibration due to resonant shaking of the housing C to occur. This resonant shaking causes the overall vibration noise of the housing C of the reverse osmosis purification unit to become stronger.

In addition to the drawback of increasing overall vibration noise of the housing C, a further drawback occurs in that the water pipe P connected on the water outlet orifice 22 of the pump head cover 20 will synchronously shake in resonance with the primary vibration (indicated by the hypothetic line a shown in FIG. 14). This synchronous shaking of the water pipe P will result in still further drawbacks by causing other rest parts of the conventional compressing diaphragm pump to simultaneously shake. As a result, after a certain period, 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 fit between other parts affected by the shaking.

The additional drawbacks of overall resonant shaking and water leakage in the S conventional compressing diaphragm pump cannot be solved by the conventional way of addressing the foregoing primary vibration drawback. I-low to substantially reduce all the drawbacks associated with the operating vibration of the compressing diaphragm pump has become an urgent and critical issue.

Summary Of The Invention

An objective is to provide a vibration-reducing structure for a compressing diaphragm pump having a pump head body and a diaphragm membrane, in which the pump head body includes three operating holes and at least one basic curved groove, slot, or perforated segment, or a curved protrusion or set of protrusions, circumferentially disposed around at least a portion of the upper side of each operating hole, and in which 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 at least one 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 each mating basic curved groove in the pump head body so that the three basic curved protrusions are completely inserted into the corresponding three basic curved grooves, slots, or perforated segments with a short length of moment arm to generating less adverse vibration-causing 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 substantiafly reduced.

Another objective is to provide a vibration-reducing structure for a compressing diaphragm pump that features a pump head body with at least three basic curved grooves, slots or perforated segments, or curved protmsions, and a diaphragm membrane with three basic curved protrusions, or curved grooves, slots, or perforated segments, such that three basic curved protrusions are completely inserted into corresponding three basic curved grooves, slots, or perforated segments with a short length of moment arm in generating less adverse vibration-causing torque, the torque being obtained by multiplying the length of the moment arm with a constant acting force. With less torque, the vibration strength of the compressing diaphragm pump is substantially reduced. Having the present invention installed on the housing of the reverse osmosis purification unit pillowed by a conventional cushion base with rubber shock absorber, the annoying noise caused by resonant shaking in the conventional compressing diaphragm pump can be completely 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 a pump head body for the conventional compressing diaphragm pump.

F 1G. 4 is a cross sectional view taken against the section line 4-4 from previous FIG. 3.

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

FIG. 6 is a perspective view of a diaphragm membrane for the conventional compressing diaphragm pump.

FIG. 7 is a cross sectional view taken against the section line 7-7 from previous FIG. 6.

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

FIG. 9 is a cross sectional view taken against the section line of 9-9 from previous FIG. 1.

FIG. 10 is the first operation illustrative view of the conventional compressing diaphragm pump.

FIG. 11 is the second operation illustrative view for conventional compressing diaphragm pump.

FIG. 12 is the third operation illustrative view of the conventional compressing diaphragm pump with a partially enlarged view of a maj or circled-portion.

FIG. 13 is a partially enlarged view taken from the circled-portion "a" in the enlarged view of previous FIG. 12.

FIG. 14 is a schematic side view showing a conventional compressing diaphragm -10-pump installed on a mounting base in a reverse osmosis purification system.

FIG. 14(a) is a schematic end view of the conventional compressing diaphragm pump installed on a mounting base, as illustrated in FIG. 14.

FIG. 15 is a perspective exploded view of the first exemplary embodiment of the present invention.

FIG. 16 is a perspective view of a pump head body in the first exemplary embodiment of the present invention.

FIG. 17 is a cross sectional view taken against the section line 17-17 from previous FIG. 16.

FIG. 18 is a top view of the pump head body in the first exemplary embodiment of the present invention.

FIG. 19 is a perspective view of a diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 20 is a cross sectional view taken against the section line 20-20 from previous FIG. 19.

FIG. 21 is a bottom view of the diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 22 is an assembled cross sectional view of the first exemplary embodiment of the present invention.

FIG. 23 is an operation illustrative view for the first exemplary embodiment of the present invention with a partially enlarged view of the major circled-portion, F 1G. 24 is a partially enlarged view taken from the circled-portion "a" in the enlarged view of previous FIG. 23.

FIG. 25 is a perspective view of another pump head body in the first exemplary embodiment of the present invention.

FIG. 26 is a cross sectional view taken against the section line 26-26 from previous FIG. 25.

FIG. 27 is a cross sectional view of another pump head body and separated diaphragm membrane in the first exemplary embodiment of the present invention.

FIG. 28 is a cross sectional view a combination of the pump head body and diaphragm membrane of FIG. 27, FIG. 29 is a perspective view of a pump head body in the second exemplary embodiment of the present invention.

FIG. 30 is a cross sectional view taken against the section line 30-30 from previous FIG. 29.

FIG. 31 is a top view of the pump head body in the second exemplary embodiment of the present invention.

FIG. 32 is a perspective view of a diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 33 is a cross sectional view taken against the section line 33-33 from previous FIG. 32.

FIG. 34 is a boftom view of a diaphragm membrane in the second exemplary -12-embodiment of the present invention.

FIG. 35 is a cross sectional view of a combination of the pump head body arid diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 36 is a perspective view for another pump head body in the second exemplary embodiment of the present invention.

FIG. 37 is a cross sectional view taken against the section line 37-37 from previous FIG. 36.

FIG. 38 is a cross sectional view of another pump head body and separated diaphragm membrane in the second exemplary embodiment of the present invention.

FIG. 39 is a cross sectional view of a combination of the pump head body and diaphragm membrane of Fig. 38.

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

FIG. 41 is a cross sectional view taken against the section line 41-4] from previous FIG. 40.

FIG. 42 is a top view of a pump head body in the third exemplary embodiment of the present invention.

FIG. 43 is a perspective view of a diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 44 is a cross sectional view taken against the section line 44-44 from previous FIG. 43.

-13 -FIG. 45 is a bottom view of a diaphragm membrane in the third exemplary embodiment of the present invention, FIG. 46 is a cross sectional view of a combination of the pump head body and diaphragm membrane in the third exemplary embodiment of the present invention.

FIG. 47 is a perspective view of another pump head body in the third exemplary embodiment of the present invention.

FIG. 48 is a cross sectional view taken against the section line 48-48 from previous FIG. 47.

FIG. 49 is a cross sectional view of another pump head body and separated tO diaphragm membrane in the third exemplary embodiment of the present invention, FIG. 50 is a cross sectional view of a combination of the pump head body and diaphragm membrane of FIG. 49.

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

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

FIG. 53 is a top view of the pump head body in the fourth exemplary embodiment of the present invention, FIG. 54 is a perspective view of a diaphragm membrane in the fourth exemplary embodiment of the present invention, FIG. 55 is a cross sectional view taken against the section line 55-55 from -14-previous FIG. 54.

FIG. 56 is a bottom view of the diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 57 is a cross sectional view of a combination of the pump head body and diaphragm membrane in the fourth exemplary embodiment of the present invention, FIG. 58 is a perspective view for another pump head body in the fourth exemplary embodiment of the present invention, FIG. 59 is a cross sectional view taken against the section line 59-59 from previous FIG. 58.

FIG. 60 is a cross sectional view of another pump head body and separated diaphragm membrane in the fourth exemplary embodiment of the present invention.

FIG. 61 is a cross sectional view of a combination of the pump head body and diaphragm membrane of FIG. 60.

FIG. 62 is a perspective view OF A pump head body in the fifth exemplary embodiment of the present invention, FIG. 63 is a cross sectional view taken against the section line of 63-63 from previous FIG. 62.

FIG. 64 is a top view of the pump head body in the fifth exemplary embodiment of the present invention.

FIG. 65 is a perspective view of the diaphragm membrane in the fifth exemplary embodiment of the present invention.

-15 -F 1G. 66 is a cross sectional view taken against the section line 66-66 from previous FIG. 65.

FIG. 67 is a bottom view for diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 68 is a cross sectional view of a combination of the pump head body and diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 69 is a perspective view of another pump head body in the fifth exemplary embodiment of the present invention.

FIG. 70 is a cross sectional view taken against the section line 70-70 from previous FIG. 69.

FIG. 71 is a cross sectional view of another pump head body and separated diaphragm membrane in the fifth exemplary embodiment of the present invention.

FIG. 72 is a cross sectional view of a combination of the pump head body and diaphragm membrane of FIG. 71.

FIG. 73 is a perspective view of a pump head body in the sixth exemplary embodiment of the present invention, FIG. 74 is a cross sectional view taken against the section line 74-74 from previous FIG. 73.

FIG. 75 is a top view of the pump head body in the sixth exemplary embodiment of the present invention.

FIG. 76 is a perspective view of the diaphragm membrane in the sixth exemplary -16-embodiment of the present invention.

FIG. 77 is a cross sectional view taken against the section line 77-77 from previous FIG. 76.

FIG. 78 is a bottom view of the diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 79 is a cross sectional view of a combination of the pump head body and diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 80 is a perspective view of another pump head body in the sixth exemplary embodiment of the present invention.

FIG. 81 is a cross sectional view taken against the section line 81-81 from previous FIG. 80.

FIG. 82 is a cross sectional view of another pump head body and separated diaphragm membrane in the sixth exemplary embodiment of the present invention.

FIG. 83 is a cross sectional view of a combination of the pump head body and diaphragm membrane of FIG. 82, FIG. 84 is a top view of a pump head body in the seventh exemplary embodiment of the present invention.

FIG. 85 is a bottom view of a diaphragm membrane in the seventh exemplary embodiment of the present invention.

FIG. 86 is a cross sectional view of a combination of the pump head body and diaphragm membrane in the seventh exemplary embodiment of the present invention. -17-

F 1G. 87 is a perspective view of another pump head body in the seventh exemplary embodiment of the present invention.

FIG. 88 is a cross sectional view taken against the section line 88-88 from previous FIG. 87.

FIG. 89 is a cross sectional view of another pump head body and separated diaphragm membrane in the seventh exemplary embodiment of the present invention.

FIG. 90 is a cross sectional view of a combination of the pump head body and diaphragm membrane of FIG. 89.

Detailed Description Of The Preferred Embodiments

FIGS. 15 through 22 are illustrative figures of a first exemplary embodiment of a vibration-reducing structure for a compressing diaphragm pump.

A basic curved groove 65 is circumferentially disposed around a portion of the upper side of each operating hole 61 in the pump head body 60 while a basic curved protrusion 77 is circumferentially disposed around a portion of each concentric annular positioning protrusion 76 at the bottom side of the diaphragm membrane 70 such that positions of the basic curved groove 65 and curved protrusion 77 correspond to each other, enabling the curved protmsion 77 to extend into and thereby mate with the basic curved groove 65.

Each of the basic curved protrusions 77 at the bottom side of the diaphragm membrane 70 is completely inserted into each of the corresponding basic curved grooves 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. 22 and associated enlarged view) with -18-the result that a short length of moment arm L2 from the basic curved protrusions 77 to the peripheral of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in FIG. 24), Referring to FIGS. 23, 24, 13, 14, and 14(a), which are illustrative figures for the practical operation result in the first exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention.

Comparing to the operation of conventional compressing diaphragm pump, the 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 in the conventional compressing diaphragm pump is shown in FIGS. 13 and 24), and the length of moment arm L2 from the basic curved protrusions 77 to the peripheral of the annular positioning protruding block 76 in the diaphragm membrane 70 obtained in the operation of the first exemplary embodiment is shown in FTG. 24.

The illustration of the foregoing comparative result shows that the length of moment arm L2 is shorter than the length of moment arm Li.

While the resultant torque is calculated by the 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 related vibration strength related is substantially reduced.

Through practical pilot testing of a sample of the present invention, the result shows that the resuhing vibration strength is only one tenth (10 %) of the vibration -19-strength in the conventional compressing diaphragm pump.

If the present invention is installed on the housing C of the reverse osmosis purification unit pillowed by a conventional cushion base 100 with a rubber shock absorber 102 (as shown in FIGS. 14 and 14(a)), the annoying noise from the resonant shaking incurred in the conventional compressing diaphragm pump can be completely eliminated.

As shown in FIGS. 25 and 26, in the first exemplary embodiment, each basic curved groove 65 of the pump head body 60 can be adapted into a basic curved s'ot or bore 64 that extends through the pump head body 60.

tO As shown in FIGS. 27 and 28, in the first exemplary embodiment, each basic curved groove 65 in the pump head body 60 (as shown in FIGS. 16 and 17) and each corresponding basic curved protmsion 77 in the diaphragm membrane 70 (as shown in FIGS. 20 md 21) can be exchmged to provide a basic curved protrusion 65t in the pump head body 60 (as shown in FIG. 27) and a corresponding basic curved groove 77t in the t5 diaphragm membrane 70 (as shown in FIG. 28) 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. 28), with the result that a short length of moment arm L3 from the basic curved indent 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 FIG. 28 and the associated enlarged view), so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect -20 -in reducing vibration as well.

Referring to FIGS. 29 through 35, which are illustrative figures for the second exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention, A second outer curved groove 66 is further circumferentially disposed around each existing basic curved groove 65 in the pump head body 60 (as shown in FIGS. 29 through 31) while a second outer curved protrusion 78 is further circumferentially disposed around each existing basic curved protrusion 77 in the diaphragm membrane 70 at a position corresponding to the position of each mating second outer curved groove 66 in the pump head body 60 (as shown in FIGS, 33 and 34).

Each pair of basic curved protrusion 77 and second outer curved protrusion 78 at the boftom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding basic curved groove 65 and second outer curved groove 66 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm tS membrane 70 (as shown in FIG. 35 and the associated enlarged view), with the result that a short length of moment arm L2 from the basic curved protrusion 77 to the peripheral of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in FIG. 35 and associated enlarged view).

The newly devised contrivances of pump head body 60 and diaphragm membrane 70 not only have a significant effect in reducing vibration, but also provide enhanced steadiness in preventing relative displacement of the pump head body 60 and diaphragm member 70 and maintaining the length of moment arm [2 for resisting against the acting force F on the eccentric roundel 52. -21 -

As shown in FIGS. 36 and 37, in the second exemplary embodiment, each pair of basic curved groove 65 and second outer curved groove 66 of the pump head body 60 can be replaced by a pair of basic curved slots or bores 64 and second outer curved slots or bores 67.

As shown in FIGS. 38 and 39, in the second exemplary embodiment, each pair of basic curved groove 65 and second outer curved groove 66 in the pump head body 60 (as shown in FIGS. 29 to 31) and each corresponding pair of basic curved protrusion 77 and second outer curved protrusion 78 in the diaphragm membrane 70 (as shown in FIGS. 33 and 34) can be exchanged with a pair of basic curved protrusion 651 and second outer curved protrusion 661 in the pump head body 60 (as shown in FIG. 28) and a pair of corresponding basic curved grove 771 and second outer curved groove 781 in the diaphragm membrane 70 (as shown in FIG. 38) without affecting their mating condition.

Each pair of basic curved protrusion 651 and second outer curved protrusion 661 at the upper side of the pump head body 60 is completely inserted into each corresponding pair of basic curved groove 771 and second outer curved groove 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. 39), 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 FIG. 39 and the associated enlarged view).

The newly devised contrivances of pump head body 60 and diaphragm membrane not only have a significant effect in reducing vibration, but also enhance steadiness by preventing relative displacement and maintaining the length of moment arm L2.

-22 -fIGS. 40 through 46 are illustrative figures for the third exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention.

A basic indented ring 601 is further circumferentially disposed around each existing operating hole ólin the pump head body 60 (as shown in FIGS. 40 through 42) while a basic protruding ring 701 is further circumferentially disposed around each existing annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating basic indented ring 601 in the pump head body (as shown in FIGS. 44 and 45).

Each basic protruding ring 701 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding basic indented ring 601 in 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. 46) with the result that a short length of moment arm L2 from the basic protruding ring 701 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. 46).

The newly devised contrivances of pump head body 60 arid diaphragm membrane not only has a significant effect in reducing vibration, but also enhances steadiness by preventing relative displacement and maintaining the length of moment arm L2 for resisting against the acting force F on the eccentric roundel 52.

As shown in FIGS. 47 and 48, in the third exemplary embodiment, each basic indented ring 601 of the pump head body 60 can be adapted into a basic perforated hole 600.

As shown in FIGS. 49 and 50, in the third exemplary embodiment, each basic -23 -indented ring 601 in the pump head body 60 (as shown in FIGS. 40 to 42) and each corresponding basic protruding ring 701 in the diaphragm membrane 70 (as shown in FIGS. 44 and 45) can be exchanged with a basic protruding ring 610 in the pump head body 60 (as shown in FIG. 27) and a corresponding basic indented ring 710 in the diaphragm membrane 70 (as shown in FIG. 50) without affecting their mating condition, Each basic protruding ring 6t0 at the upper side of the pump head body 60 is completely inserted into each corresponding basic indented ring 710 at the boftom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 50) with the result that a short length of moment arm L3 from the basic indented ring 710 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. 50) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration as well.

FIGS. 51 through 57 are illustrative figures for the fourth exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention.

A pair of curved indented segments 602 is further circumferentially disposed around each existing operating hole 61 in the pump head body 60 (as shown in FIGS. 51 through 53) while a pair of curved protruding segments 702 is further circumferentially disposed around each existing annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating curved indented segment 602 in the pump head body 60 (as shown in FIGS. 55 and 56).

Each pair of curved protruding segments 702 at the bottom side of the diaphragm -24 -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. 57) 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 in the operation of the present invention (as shown in FIG. 57).

The newly devised contrivances of pump head body 60 and diaphragm membrane not only have a significant effect in reducing vibration but also enhance steadiness by preventing relative displacement and maintaining the length of moment arm L2.

As shown in FIGS. 58 and 59, 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. 60 and 61, in the fourth exemplary embodiment, each pair of curved indented segments 602 in the pump head body 60 (as shown in FIGS. St to 53) and each corresponding pair of curved protmding segments 702 in the diaphragm membrane 70 (as shown in FIGS. 55 and 56) can be exchanged with a pair of curved protmding segments 620 in the pump head body 60 (as shown in FIG. 60) and a pair of corresponding curved indented segments 720 in the diaphragm membrane 70 (as shown in FIG. 6t) 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. 61) with the result that a -25 -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 in the operation of the present invention (as shown in FIG. 61) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have a significant effect in reducing vibration as well.

FIGS. 62 through 68 are illustrative figures for the fifth exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention.

A group of round indents 603 are further circumferentially disposed around each existing operating hole 61 in the pump head body 60 (as shown in FIGS. 62 through 64) while a group of round protrusions 703 are further circumferentially disposed around each existing annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding position corresponding to the position of each group of mating round indents 603 in the pump head body 60 (as shown in FIGS. 66 and 67).

Each group of round protrusions 703 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of round indents 603 at the upper side of the pump head body 60 npon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in FIG. 68) 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 also shown in FIG. 68).

The newly devised contrivances of pump head body 60 and diaphragm membrane not only have significant effect in reducing vibration as well but also enhance the steadiness by preventing relative disp'acement and maintaining the ength of moment arm -26 -L2.

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

As shown in FIGS. 71 and 72, in the fifth exemplaty embodiment, each group of round indents 603 in the pump head body 60 (as shown in FIGS. 62 to 64) and each corresponding group of round protrusions 703 in the diaphragm membrane 70 (as shown in FIGS. 66 and 67) can be exchanged with a group of round protrusions 630 in the pump head body 60 (as shown in FIG. 71) and a group of corresponding round indents 730 in the diaphragm membrane 70 (as shown in FIG. 71) 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 indents 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. 72) with the result that a short length of moment arm L3 from the round indents 730 to the peripheiy 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. 72) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have significant effect in reducing vibration as well.

FIGS. 73 through 79 are illustrative figures for the sixth exemplary embodiment of the vibration-reducing structure for compressing diaphragm pump of the present invention.

A group of square indents 604 are tbrther circumferentially disposed around each existing operating hole 61 in the pump head body 60 (as shown in FIGS. 73 through 75) while a group of square protrusions 704 are further circumferentially disposed around each existing annular positioning protrusion 76 in the diaphragm membrane 70 in a corresponding position with each mating group of square indents 604 in the pump head body 60 (as shown in FIGS. 77 and 78).

Each group of square protrusions 704 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of square indents 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. 79 and enlarged view of association) 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 in the operation of the present invention (as shown in FIG. 79 and enlarged view of association).

The newly devised contrivances of pump head body 60 and diaphragm membrane 70 not only have a significant effect in reducing vibration but a'so enhance steadiness by preventing relative displacement and maintaining the length of moment arm L2.

As shown in FIGS. 80 and 81, in the sixth exemplary embodiment, each group of square indents 604 in the pump head body 60 can be replaced by a group of square perforated holes 613, As shown in FIGS. 82 and 83 in the sixth exemplary embodiment, each group of square indents 604 in the pump head body 60 (as shown in FIGS. 73 to 75) and each corresponding group of square protrusions 704 in the diaphragm membrane 70 (as shown in FIGS. 77 and 78) can be exchanged with a group of square protrusions 640 in the pump -28 -head body 60 (as shown in FIG. 82) and a group of corresponding square indents 740 in the diaphragm membrane 70 (as shown in FIG. 82) 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 indents 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. 83) with the result that a short length of moment arm [3 from the square indents 740 to the periphery of the annular positioning protrusion 76 in the diaphragm membrane 70 is also obtained in the operation of the to present invention (as shown in FIG. 83 and enlarged view of association) so that the newly devised contrivances of pump head body 60 and diaphragm membrane 70 have significant effect in reducing vibration as well.

FIGS. 84 through 86 are illustrative figures for the seventh exemp'ary embodiment of the vibration-reducing stmcture for compressing diaphragm pump of the present invention.

A pair of concentric first inner indented ring 605 and second outer indented ring 606 are further circumferentially disposed around each existing operating hole 61 in the pump head body 60 (as shown in FIG. 84) while a pair of concentric first inner protruding ring 705 and second outer protruding ring 706 are further circumferentially disposed around each existing annular positioning protrusion 76 in the diaphragm membrane 70 at a position corresponding to a position of each mating pair of first inner indented ring 605 and second outer indented ring 606 in the pump head body 60 (as shown in FIG. 85).

Each pair of first inner protruding ring 705 and second outer protruding ring 706 at -29 -the boftom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding first inner indented ring 605 and second outer indented ring 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. 86) with the result that a short length of moment arm L2 from the first inner protmding ring 705 to the peripheral of the annular positioning protrusion 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in FIG. 86).

The newly devised contrivances of pump head body 60 and diaphragm membrane not only have significant effect in reducing vibration but also enhance steadiness by preventing relative displacement and maintaining the length of moment arm L2 for resisting against the acting force F on the eccentric roundel 52.

As shown in FIGS. 87 and 88, in the seventh exemplary embodiment, each pair of concentric first inner indented ring 605 and second outer indented ring 606 in the pump head body 60 can be replaced by a pair of concentric first inner perforated ring 614 and second outer perforated ring 615, As shown in FIGS. 89 and 90, in the seventh exemplary embodiment, each pair of concentric first inner indented ring 605 and second outer indented ring 606 in the pump head body 60 (as shown in FIG. 84) and each corresponding pair of concentric first inner protruding ring 705 and second outer protruding ring 706 in the diaphragm membrane 70 (as shown in FIGS. 77 and 78) can be exchanged with a pair of concentric first inner protruding ring 650 and second outer protruding ring 660 in the pump head body 60 (as shown in FIG. 89) and a corresponding pair of concentric first inner indented ring 750 and second outer indented ring 760 in the diaphragm membrane 70 (as shown in FIG. 89) -30 -without affecting their mating condition.

Each pair of first inner protruding ring 650 and second outer protruding ring 660 at the upper side of the pump head body 60 completely is inserted into each corresponding pair of first inner indented ring 750 and second outer indented ring 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. 90) with the result that a short length of moment arm L3 from the first inner indented ring 750 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. 90).

The newly devised contrivances of pump head body 60 and diaphragm membrane not only have significant effect in reducing vibration, but also enhance steadiness by preventing relative displacement and maintaining the length of moment arm L3.

Based on the foregoing disclosure, the present invention substantially achieves the vibration reducing effect of the compressing diaphragm pump by means of simple newly devised pump head body 60 and diaphragm membrane 70 without increasing overall cost.

The present invention surely solves all issues of noise and resonant shaking to which the conventional compressing diaphragm pump is subject, and thus the invention has valuable

industrial applicability. -31 -