JP6124089B2 - Multi-effect type diaphragm pump - Google Patents

Description

  The present invention relates to a multi-effect pressure-feeding diaphragm pump used in a reverse osmosis (RO) purification system, and more particularly to reduce unnecessary noise and vibration due to resonance in a conventional pressure-feeding diaphragm pump. Inclined top ring that has an innovative means of fitting diaphragm membrane and can eliminate the oblique tension and compression phenomenon of the pump so as to lengthen the service life of the pumping diaphragm pump and the durability of its main parts The present invention relates to a pressure-feeding diaphragm pump included in an eccentric roundel mount.

  Conventional pressure-feeding diaphragm pumps of the type commonly used in RO (reverse osmosis) purifiers or RO water purification systems are Patent Document 1, Patent Document 2, Patent Document 3, Patent Document 4, Patent Document 5, Patent Document 6, Patent It is disclosed in Document 7, Patent Document 8, and Patent Document 9. An example of a conventional pressure-feeding diaphragm pump is shown in FIGS. 1 to 10, which basically includes a motor 10 with a brush having an output shaft 11, a motor upper chassis 30, and a wobble having a shaft with a cam lobe protruding integrally therewith. A plate 40, an eccentric roundel mount 50, a pump head body 60, a diaphragm membrane 70, three pumping pistons 80, a piston valve assembly 90, and a pump head cover 20 are provided.

  The motor upper chassis 30 has a bearing 31 through which the output shaft 11 of the motor 10 passes. The motor upper chassis 30 further includes an upper annular rib ring 32, and a plurality of fastening holes 33 are evenly arranged in the circumferential direction on the periphery of the upper annular rib ring 32.

  The wobble plate 40 has a shaft coupling hole 41 through which the corresponding motor output shaft 11 of the motor 10 extends.

  The eccentric roundel mount 50 has a central bearing 51 at its bottom for receiving a corresponding wobble plate 40. On the eccentric roundel mount 50, three tubular eccentric roundels 52 are arranged equally in the circumferential direction. Each tubular eccentric roundel 52 is formed at the intersection of the horizontal top surface 53, the female screw hole 54, the annular positioning groove 55 formed on the top surface, and the horizontal top surface 53 and the vertical side portion 56. It has a round shoulder 57.

  The pump head main body 60 covers the upper annular rib ring 32 of the motor upper chassis 30 and surrounds the wobble plate 40 and the eccentric roundel mount 50 therein. Two operating holes 61 are provided. Each actuation hole 61 has an inner diameter that is slightly larger than the outer diameter of the corresponding tubular eccentric roundel 52 in the eccentric roundel mount 50 for receiving an individual corresponding tubular eccentric roundel 52, respectively, In order to mate with the corresponding upper annular rib ring 32 of the upper chassis 30, it has a lower annular flange 62 formed on the lower side thereof and a plurality of fastening holes 63 arranged evenly around the pump head body 60.

  The diaphragm membrane 70 is extruded from a semi-rigid elastic material and disposed on the pump head body 60, and includes a pair of parallel rims including an outer rising rim 71 and an inner rising rim 72, and 3 Each of the radial rising partition ribs 73 is connected to the inner rising rim 72 so that the three equal rising partition ribs 73 are separated by the radial rising partition ribs 73. Piston actuation zones 74 are formed within those ranges, and each piston actuation zone 74 is formed therein corresponding to an individual female threaded hole 54 in the tubular eccentric roundel 52 of the eccentric roundel mount 50. Each of the working zone holes 75 (as shown in FIGS. 9 and 10) on the bottom side of the diaphragm membrane 70. And an annular positioning projection 76 is formed.

  Each pumping piston 80 is disposed within an individual corresponding piston actuation zone 74 of the diaphragm membrane 70 and has a stepped hole 81 extending therethrough. After each of the annular positioning projections 76 in the diaphragm membrane 70 is inserted into the corresponding annular positioning recess 55 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, the individual fastening screws 1 are inserted into the stepped holes of each pumping piston 80. 81 and the diaphragm membrane 7 are inserted through the actuation zone holes 75 of the corresponding respective piston actuation zones 74 so that the diaphragm membrane 70 and the three pumping pistons 80 (as shown in the enlarged part of FIG. 11). ) It can be screwed into the female screw holes 54 of the corresponding three tubular eccentric roundels 52 in the eccentric roundel mount 50.

  The piston valve assembly 90 covers the diaphragm membrane 70 and rises downward to be inserted into the spacing ring between the outer rising rim 71 and the inner rising rim 72 in the diaphragm membrane 70. 91, a central circular dish-shaped outlet mount 92 with a central positioning hole 93 and three equivalent sectors each including a plurality of outlet ports 95 equally distributed in the circumferential direction, T with a central positioning shank Mold plastic backflow prevention valve 94 and three circumferentially adjacent inlet mounts 96. Each of the circumferentially adjacent inlet mounts 96 includes a plurality of inlet ports 97 and an inverted central piston disk 98 that are equally disposed in the circumferential direction, and each piston disk 98 includes a plurality of inlet ports 97. Functions as a valve for each corresponding group. The central positioning shank of the plastic backflow check valve 94 fits into the central positioning hole 93 of the central outlet mount 92, the plurality of outlet ports 95 in the central circular outlet mount 92 communicate with the three inlet mounts 96, and When the rising rim 91 extending downward is inserted into the spacing ring between the outer rising rim 71 and the inner rising rim 72 of the diaphragm membrane 70, the corresponding piston actuation in each inlet mount 96 and diaphragm membrane 70 A sealed precompression chamber 26 is formed between the zones 74 and one end of each precompression chamber 26 communicates with each of the corresponding inlet ports 97 (as shown in the enlarged portion of FIG. 11).

  The pump head cover 20 covers the pump head body 60 and surrounds the piston valve assembly 90, the pumping piston 80, and the diaphragm membrane 70. The pump head cover 20 includes a water inlet orifice 21, a water outlet orifice 22, and a plurality of them. The fastening hole 23 is provided. A stepped rim 24 and an annular rib ring 25 are arranged inside the bottom of the pump head cover 20, and the outer rim of the assembly comprising the diaphragm membrane 70 and the piston valve assembly 90 (as shown in the enlarged portion of FIG. 11). It can be hermetically mounted on the stepped rim 24. When the bottom of the annular rib ring 25 closes and covers the periphery of the central outlet mount 92 (as shown in FIG. 11), the cavity formed by the inner wall of the annular rib ring 25 and the central outlet mount 92 of the piston valve assembly 90 In between, the high compression chamber 27 is formed.

  The fastening bolts 2 are respectively inserted into the corresponding fastening holes 23 of the pump head cover 20 and the corresponding fastening holes 63 of the pump head main body 60, and the nuts 3 are arranged on the respective fastening bolts 2, so that the corresponding fastening in the motor upper chassis 30 is performed. When the pump head cover 20 is screwed to the pump head body 60 through the holes 33, the entire assembly of the pumping diaphragm pump is completed (as shown in FIGS. 1 and 11).

  Reference is made to FIGS. 12 and 13 which are explanatory views of the operation of the conventional pressure-feeding diaphragm pump of FIGS.

  First, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11, so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 are continuously reciprocated vertically. Stroke operation.

  Secondly, in the meantime, the three pumping pistons 80 and the three piston operation zones 74 in the diaphragm membrane 70 are sequentially driven by the up and down reciprocating strokes of the three tubular eccentric roundels 52 to be displaced up and down.

  Third, when the tubular eccentric roundel 52 performs a downward stroke operation to displace the pumping piston 80 and the piston operating zone 74 downward, the piston disk 98 in the piston valve assembly 90 is pushed to the open state, and the tap water W Can flow into the precompression chamber 26 through the inlet orifice 21 of the pump head cover 20 and the inlet port 97 of the piston valve assembly 90 (as shown by the arrow extending from W in the enlarged view of FIG. 12).

  Fourth, when the tubular eccentric roundel 52 moves up and displaces the pumping piston 80 and the piston operating zone 74, the piston disk 98 in the piston valve assembly 90 is pulled to the closed state, and the precompression chamber The tap water W in 26 is compressed, and the water pressure therein is increased to a range of 80 psi to 100 psi. The resulting pressurized water Wp pushes the plastic backflow prevention valve 94 in the piston valve assembly 90 to the open state.

  Fifth, when the plastic backflow prevention valve 94 in the piston valve assembly 90 is pushed to the open state, the pressurized water Wp in the precompression chamber 26 is removed from the central outlet mount 92 (as indicated by the arrow W in the enlarged portion of FIG. 13). To the high compression chamber 27 through a group of outlet ports 95 for the corresponding sector and then discharged from the outlet orifice 22 in the pump head cover 20.

  Finally, by repeated operation for each group of three sector outlet ports 95 in the central outlet mount 92, the pressurized water Wp is continuously discharged from the conventional pumping diaphragm pump and further RO filtered by the RO cartridge. Thus, the final filtered pressurized water Wp can be used in the reverse osmosis water purification system.

U.S. Pat. No. 4,396,357 US Pat. No. 4,610,605 US Pat. No. 5,476,367 US Patent No. 5571000 US Pat. No. 5,615,597 US Pat. No. 5,649,812 US Pat. No. 5,706,715 US Pat. No. 5,791,882 US Pat. No. 5,816,133

  Referring to FIGS. 14-16, the conventional pumping diaphragm pump has significant vibration-related drawbacks that have existed for a long time. As described above, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11, so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 are continuously and vertically moved. In the meantime, the three pumping pistons 80 and the three piston operating zones 74 in the diaphragm membrane 70 are driven by the up and down reciprocating strokes of the three tubular eccentric roundels 52 in the meantime, thereby moving up and down. Thus, an equivalent force F always acts on the three piston operating zones 74 with the moment arm length L1 measured from the outer rising rim 71 to the periphery of the annular positioning projection 76 (as shown in FIG. 15). To do. Thus, a composite torque is generated by multiplying the acting force F by the moment arm length L1 by the expression “torque = acting force F × moment arm length L1”. This combined torque directly vibrates the entire conventional diaphragm pump. The vibration intensity generated by the three tubular eccentric roundels 52 operating alternately by the high-speed rotation of the motor output shaft 11 in the motor 10 in the range of 700 to 1200 rpm can reach an unacceptable state continuously.

  In order to cope with the shortcomings of the conventional pressure-feeding diaphragm pump, as shown in FIG. 16, a cushion base 100 having a pair of blade plates 101 is always provided as an auxiliary support. In order to enhance the suppression, a sleeve made of rubber cushioning material 102 is further mounted. When installing a conventional pressure-feeding diaphragm pump, the cushion base 100 is screwed to the housing C of the reverse osmosis purification unit by means of an appropriate fastening screw 103 and a corresponding nut 104. However, the actual vibration suppression efficiency by the cushion base 100 including the blade plate 101 and the rubber cushioning material 102 only reduces noise due to primary vibration, and noise due to secondary vibration generated as a result of resonance vibration of the housing C. Has no effect. Secondary vibrations actually increase the overall vibration noise of the housing C of the reverse osmosis purification unit.

  In addition to the disadvantage that the overall vibration noise of the housing C increases, the water pipe P connected to the outlet orifice 22 of the pump head cover 20 resonates with the vibration (in FIGS. 16 and 16a, the water pipe P A further disadvantage arises of synchronous oscillation (as indicated by the broken line). As a result of this synchronous vibration of the water pipe P, further disadvantages arise due to simultaneous vibrations in other parts of the conventional pumping diaphragm pump. As a result, the connection between the water supply pipe P and the outlet orifice 22 is gradually loosened, and the fitting between other parts affected by vibration is gradually loosened. Water leakage occurs. The additional disadvantages of overall resonant vibration and water leakage in conventional pumping diaphragm pumps cannot be solved by the above-described conventional method of dealing with primary vibrations using the cushion cushion base 100. Therefore, it is an urgent and important issue how to alleviate all of the drawbacks related to the vibration of the pumping diaphragm pump.

  Figures 17 and 18 illustrate yet another problem with a conventional diaphragm pump. As described above, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11, so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 are continuously and vertically moved. The three piston operation zones 74 in the diaphragm membrane 70 are driven by the vertical reciprocation strokes of the three tubular eccentric roundels 52 to move up and down, thereby moving each piston operation zone. The force F always acts on the bottom side of 74.

  On the other hand, a plurality of corresponding reaction forces Fs are generated with respect to the acting force F applied to the bottom side of the diaphragm film 70, and a compression phenomenon caused by the reaction force Fs occurs in a part of the diaphragm film 70 as shown in FIG. Thus, different components are dispersed throughout the bottom area of each of the corresponding piston actuation zones 74 in the diaphragm membrane 70.

  Of all the dispersion components of the reaction force Fs, the maximum component force acts on the bottom surface position P where the diaphragm film 70 contacts the round shoulder 57 of the horizontal top surface 53 in the tubular eccentric roundel 52, and as shown in FIG. Thus, the compression phenomenon at the bottom surface position P is also maximized.

  When the rotational speed of the motor output shaft 11 of the motor 10 reaches the range of 700 to 1200 rpm, the bottom surface position P of the piston operation zone 74 of the diaphragm film 70 is subjected to a compression phenomenon at a frequency of four times per second. Under such circumstances, the bottom surface position P of the diaphragm membrane 70 is always the first breakage point in the entire conventional pressure-feeding diaphragm pump, which not only shortens the service life, but also normal operation of the conventional pressure-feeding diaphragm pump. This is the root cause of the malfunction.

  Thus, how to greatly mitigate the disadvantages associated with compression phenomena due to the constant force F acting on the bottom side of each piston actuation zone 74 of the diaphragm membrane 70 as a result of the operation of the tubular eccentric roundel 52. It is also an urgent and important issue.

  An object of the present invention is to provide a multi-effect pressure-feeding diaphragm pump, which has an innovative fitting means between a pump head body and a diaphragm membrane, and the pump head body has three working holes, And a base curved groove, slot or perforated segment, or curved projection or group of projections, at least partially circumferentially disposed around the upper side of each actuation hole, while the diaphragm membrane has three equivalents Piston operating zones, each having an operating zone hole, an annular positioning projection for each operating zone hole, and at least partially circumferentially around each concentric annular positioning projection, and the pump head body Corresponding to the position of the corresponding base curved groove, slot, or perforated segment, or curved projection or group of projections With a base curved protrusion or group of protrusions, or grooves, slots, or perforated segments, which results in less torque generated by multiplying the moment arm length by a constant force Thus, with a short moment arm length, three base curved protrusions, protrusion groups, grooves, slots or perforated segments have corresponding three base curved grooves, slots, perforated segments, protrusions or protrusions in the pump head body The group is either fully inserted or accepted. Due to the smaller torque, the vibration strength of the pressure-feeding diaphragm pump is greatly reduced.

  Another object is to provide a multi-effect pressure-feeding diaphragm pump, which has an innovative fitting means between the pump head body and diaphragm membrane, the pump head body comprising three base curved grooves, Slots, or perforated segments, or curved protrusions or groups of protrusions, while the diaphragm membrane has three base curved protrusions or groups of protrusions, or grooves, slots, or perforated segments, thereby providing moment arms Three base curved projections or groups of projections, or grooves, slots, or perforated segments with corresponding moment arm lengths, so that the generation of torque obtained by multiplying the length by a constant acting force is smaller 3 base curved grooves, slots, or perforated segments, or curved projections or groups of projections, completely Either input, or received. Due to the smaller torque, the vibration strength of the pressure-feeding diaphragm pump is greatly reduced. When the present invention is installed in the housing of a reverse osmosis purification unit that is buffered by a conventional cushion base equipped with a rubber cushioning material in a water supply device in either a house or a mobile house, resonance vibration that has occurred in a conventional pressure-feeding diaphragm pump The unpleasant noise caused by can be completely eliminated.

  It is a further object of the present invention to provide a multi-effect pumped diaphragm pump that includes a cylindrical eccentric roundel disposed in an eccentric roundel mount. The cylindrical eccentric roundel has an annular positioning groove, a vertical side, and an annular top surface portion that is inclined relative to the horizontal to form an inclined top ring between the annular positioning groove and the vertical side. According to the inclined top ring, since the inclined top ring is mounted flat on the bottom area of the corresponding piston operating zone of the diaphragm membrane, the high-frequency oblique tension and compression phenomenon that occurs in the conventional tubular eccentric roundel is completely eliminated. The This not only improves the durability of the diaphragm membrane, but also greatly extends the useful life of the diaphragm membrane to better withstand the sustained high frequency pumping action of the eccentric roundel.

  Yet another object of the present invention is to provide a multi-effect pumped diaphragm pump, which comprises a cylindrical eccentric roundel disposed on an eccentric roundel mount. The cylindrical eccentric roundel has an annular positioning groove, a vertical side, and an inclined top ring formed between the annular positioning groove and the vertical side. According to the tilted top ring, since the tilted top ring is mounted flat on the bottom area of the corresponding piston operating zone of the diaphragm membrane, the reaction force generated against the cylindrical eccentric roundel under the action force of the pumping action All dispersed components of are significantly reduced.

By achieving the above object, at least the following effects can be obtained, although not limited thereto.
1. The durability of the diaphragm membrane against the sustained high frequency pumping action of the cylindrical eccentric roundel is greatly improved.
2. Less current is wasted as a result of the high frequency compression phenomenon described above, thereby significantly reducing the power consumption of the pressure diaphragm pump.
3. Due to the reduced power consumption, the operating temperature of the pressure diaphragm pump is significantly reduced.
4). The unpleasant noise of the bearing due to the aging of the lubricant in the pumping diaphragm pump, which is rapidly accelerated by the high operating temperature, is largely eliminated.

FIG. 1 is an assembled perspective view of a conventional pressure-feeding diaphragm pump. FIG. 2 is an exploded perspective view of a conventional pressure-feeding diaphragm pump. FIG. 3 is a perspective view of an eccentric roundel mount for a conventional pressure-feeding diaphragm pump. 4 is a cross-sectional view taken along the section line 4-4 of FIG. FIG. 5 is a perspective view of a pump head main body for a conventional pressure-feeding diaphragm pump. 6 is a cross-sectional view taken along section line 6-6 of FIG. FIG. 7 is a top view of a pump head body for a conventional pressure-feeding diaphragm pump. FIG. 8 is a perspective view of a diaphragm membrane for a conventional pressure-feeding diaphragm pump. FIG. 9 is a cross-sectional view taken along the section line 9-9 of FIG. FIG. 10 is a bottom view of a diaphragm membrane for a conventional pressure-feeding diaphragm pump. FIG. 11 is a cross-sectional view taken along section line 11-11 of FIG. FIG. 12 is a first operation explanatory diagram of a conventional pressure-feeding diaphragm pump. FIG. 13 is a diagram illustrating a second operation of the conventional pressure-feeding diaphragm pump. FIG. 14 is a diagram illustrating a third operation of the conventional pressure-feeding diaphragm pump. FIG. 15 is a partially enlarged view of a portion a encircled in FIG. FIG. 16 is a schematic view showing a conventional pressure-feeding diaphragm pump installed on a mounting base of a reverse osmosis (RO) purification system. FIG. 17 is a diagram illustrating a fourth operation of the conventional pressure-feeding diaphragm pump. FIG. 18 is a partially enlarged view of a portion b surrounded by a circle in FIG. FIG. 19 is an exploded perspective view of 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. 21 is a cross-sectional view taken along section line 21-21 of FIG. FIG. 22 is a top view of the 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. 24 is a cross-sectional view taken along section line 24-24 of FIG. FIG. 25 is a bottom view of the diaphragm membrane in the first exemplary embodiment of the present invention. FIG. 26 is a perspective view of an eccentric roundel mount in the first exemplary embodiment of the present invention. 27 is a cross-sectional view taken along section line 27-27 of FIG. FIG. 28 is an assembled cross-sectional view of the first exemplary embodiment of the present invention. FIG. 29 is a first operation explanatory diagram of the first exemplary embodiment of the present invention. FIG. 30 is a partially enlarged view of a portion a encircled in FIG. FIG. 31 is a second operation explanatory diagram of the first exemplary embodiment of the present invention. FIG. 32 is a partial enlarged view of a portion b surrounded by a circle in FIG. FIG. 33 is an explanatory cross-sectional view showing a comparison between a cylindrical eccentric roundel acting on a diaphragm membrane of a conventional pressure-feeding diaphragm pump and that of the first exemplary embodiment of the present invention. FIG. 34 is a perspective view of an adapted pump head body in the first exemplary embodiment of the present invention. 35 is a cross-sectional view taken along section line 35-35 of FIG. FIG. 36 is an exploded cross-sectional view showing a compatible pump head body and diaphragm membrane in the first exemplary embodiment of the present invention. FIG. 37 is an assembled cross-sectional view showing 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. 39 is a cross-sectional view taken along section line 39-39 of previous FIG. FIG. 40 is a top view of a pump head body in the second exemplary embodiment of the present invention. FIG. 41 is a perspective view of a diaphragm membrane in the second exemplary embodiment of the present invention. 42 is a cross-sectional view taken along section line 42-42 of FIG. FIG. 43 is a bottom view of a diaphragm membrane in the second exemplary embodiment of the present invention. FIG. 44 is an assembled cross-sectional view showing the diaphragm membrane and 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. 46 is a cross-sectional view taken along section line 46-46 of FIG. FIG. 47 is an exploded cross-sectional view showing a compatible pump head body and diaphragm membrane in a second exemplary embodiment of the present invention. FIG. 48 is an assembled cross-sectional view showing an adapted pump head body and diaphragm membrane in a 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. 50 is a cross-sectional view taken along section line 50-50 of previous FIG. 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. 53 is a cross-sectional view taken along section line 53-53 of previous FIG. FIG. 54 is a bottom view of a diaphragm membrane in the third exemplary embodiment of the present invention. FIG. 55 is an assembled cross-sectional view showing the diaphragm membrane and 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. 57 is a cross-sectional view taken along section line 57-57 of previous FIG. FIG. 58 is an exploded cross-sectional view showing an adapted pump head body and diaphragm membrane in a third exemplary embodiment of the present invention. FIG. 59 is an assembled cross-sectional view showing an adapted pump head body and diaphragm membrane in a 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. 61 is a cross-sectional view taken along section line 61-61 of previous FIG. 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. 64 is a cross-sectional view taken along section line 64-64 of previous FIG. FIG. 65 is a bottom view of a diaphragm membrane in the fourth exemplary embodiment of the present invention. 66 is an assembled cross-sectional view showing the diaphragm membrane and pump head body for the fourth exemplary embodiment of the present invention. FIG. 67 is a perspective view of an adapted pump head body in the fourth exemplary embodiment of the present invention. 68 is a cross-sectional view taken along section line 68-68 of previous FIG. FIG. 69 is an exploded cross-sectional view showing an adapted pump head body and diaphragm membrane in a fourth exemplary embodiment of the present invention. FIG. 70 is an assembled cross-sectional view showing an adapted pump head body and diaphragm membrane in a 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. 72 is a cross-sectional view taken along section line 72-72 of previous FIG. 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. 75 is a cross-sectional view taken along section line 75-75 of previous FIG. FIG. 76 is a bottom view of a diaphragm membrane in the fifth exemplary embodiment of the present invention. FIG. 77 is an assembled cross-sectional view showing the diaphragm membrane and 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. 79 is a cross-sectional view taken along section line 79-79 of previous FIG. FIG. 80 is an exploded cross-sectional view showing an adapted pump head body and diaphragm membrane in a fifth exemplary embodiment of the present invention. FIG. 81 is an assembled cross-sectional view showing 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. 83 is a cross-sectional view taken along section line 83-83 of FIG. 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. 86 is a cross-sectional view taken along section line 86-86 of previous FIG. FIG. 87 is a bottom view of a diaphragm membrane in the sixth exemplary embodiment of the present invention. 88 is an assembled cross-sectional view showing the diaphragm membrane and pump head body for the sixth exemplary embodiment of the present invention. FIG. 89 is a perspective view of an adapted pump head body in the sixth exemplary embodiment of the present invention. 90 is a cross-sectional view taken along section line 90-90 of previous FIG. FIG. 91 is an exploded cross-sectional view showing a compatible pump head body and diaphragm membrane in the sixth exemplary embodiment of the present invention. FIG. 92 is an assembled cross-sectional view showing an adapted pump head body and diaphragm membrane in a 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 an assembled cross-sectional view showing the diaphragm membrane and 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. 97 is a cross-sectional view taken along section line 97-97 of previous FIG. 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 an assembled cross-sectional view showing 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. 101 is a cross-sectional view taken along section line 101-101 of previous FIG. FIG. 102 is an assembled cross-sectional view showing the diaphragm membrane and pump head body for the eighth exemplary embodiment of the present invention. FIG. 103 is an operation explanatory diagram for the eighth exemplary embodiment of the present invention. FIG. 104 is a partially enlarged view of a portion a encircled in FIG. 103. FIG. 105 is an explanatory cross-sectional view showing a comparison of a cylindrical eccentric roundel acting on the diaphragm membrane in the case of the conventional pressure-feeding diaphragm pump and the case of the present invention in the eighth exemplary embodiment of the present invention. FIG. 106 is an exploded perspective view showing a cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention. 107 is a cross-sectional view taken along section line 107-107 of FIG. FIG. 108 is an assembled perspective view showing an adapted cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention. 109 is a cross-sectional view taken along section line 109-109 of FIG. FIG. 110 is a cross-sectional view illustrating a conforming cylindrical eccentric roundel for an eighth exemplary embodiment of the present invention. FIG. 111 is an operational illustration showing an adapted cylindrical eccentric roundel for the eighth exemplary embodiment of the present invention. FIG. 112 is a partially enlarged view of a portion a encircled in FIG. 111. FIG. 113 is an operation explanatory cross-sectional view showing a comparison of an adaptive cylindrical eccentric roundel acting on the diaphragm membrane in the case of the conventional pressure-feeding diaphragm pump and the case of the present invention in the eighth exemplary embodiment of the present invention. is there.

  19-28 are illustrations of a multi-effect pumping diaphragm pump according to a first exemplary embodiment of the present invention.

  A base curved groove 65 is circumferentially arranged around the upper side of each of the operation holes 61 in the pump head body 60, while a base curved projection 77 is formed on each of the concentric annular positioning projections 76 on the bottom side of the diaphragm film 70. Are arranged in the circumferential direction and at positions corresponding to the positions of the respective base curved grooves 65 for fitting in the pump head main body 60.

  Thereby, when the pump head main body 60 and the diaphragm membrane 70 are assembled, each of the base curved projections 77 on the bottom side of the diaphragm membrane 70 corresponds to the corresponding base on the upper side of the pump head main body 60 (as shown in FIG. 28). Each of the curved grooves 65 is completely inserted. As a result, in the operation of the present invention, a short moment arm length L2 from the base curved protrusion 77 to the periphery of the annular positioning protrusion 76 in the diaphragm film 70 is obtained (as shown in the enlarged portion of FIG. 28).

  Also, the cylindrical eccentric roundel 52 in the eccentric roundel mount 50 is horizontal (as shown in FIGS. 26 and 27) so as to form an inclined top ring 58 between the annular positioning groove 55 and the vertical side 56. The sloped top ring 58 replaces the conventional round shoulder 57 in each of the tubular eccentric roundels 52 of the eccentric roundel mount 50.

  29, 30, 15, and 16 are explanatory diagrams for the operation of the multi-effect pressure-feeding diaphragm pump of the first exemplary embodiment of the present invention.

  In the operation of the conventional pressure-feeding diaphragm pump, as shown in FIG. 15, a moment arm length L1 from the outer rising rim 71 of the diaphragm membrane 70 to the periphery of the annular positioning projection block 76 is obtained. On the other hand, in the operation of the present invention, as shown in FIG. 30, a shorter moment arm length L2 from the base curved protrusion 77 to the periphery of the annular positioning protrusion block 76 in the diaphragm film 70 is obtained.

  Since the combined torque is calculated by multiplying the same acting force F by the moment arm length, the combined torque of the present invention is that of the conventional pumping diaphragm pump because the moment arm length L2 is shorter than the moment arm length L1. Smaller than. Due to the smaller combined torque of the present invention, the vibration intensity associated therewith is greatly reduced.

  In the practical test using the prototype of the present invention, the vibration intensity was reduced to only one-tenth (10%) of the vibration intensity in the conventional pumping diaphragm pump.

  As shown in FIG. 16, when the present invention is installed in the housing C of the reverse osmosis purification unit buffered by the conventional cushion base 100 provided with the rubber cushioning material 102, unnecessary noise due to resonance vibration generated by the conventional pressure-feeding diaphragm pump. Can be completely eliminated.

  31 to 33 are explanatory diagrams for the operation of the multi-effect pressure-feeding diaphragm pump in the first exemplary embodiment of the present invention.

  First, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11, so that the three cylindrical eccentric roundels 52 on the eccentric roundel mount 50 are continuously moved up and down sequentially. Reciprocating stroke operation.

  Secondly, the three piston operation zones 74 in the diaphragm membrane 70 are driven up and down by the up and down reciprocating strokes of the three cylindrical eccentric roundels 52, thereby moving up and down.

  Thirdly, when the conventional tubular eccentric roundel 52 or the cylindrical eccentric roundel 52 of the present invention operates in the upward stroke to displace the piston operating zone 74 upward, the acting force F corresponds to the diaphragm membrane 70. A portion between the annular positioning protrusion 76 and the outer rising rim 71 is partially pulled obliquely.

  Comparing the operation of the conventional tubular eccentric roundel 52 shown in FIG. 18 and the cylindrical eccentric roundel 52 of the present invention as shown in FIG. 32, at least the following two differences are apparent.

  In the case of the conventional tubular eccentric roundel 52 shown in FIG. 18, the largest one of all the dispersion components Fs of the reaction force is located at the edge of the round shoulder 57 on the horizontal top surface 53 of the tubular eccentric roundel 52. This is a component force acting on the bottom surface position P in contact with 70, and the “compression phenomenon” at this point P is also maximized. In such a non-linear distribution of the “compression phenomenon”, the oblique tension action becomes significant. On the other hand, in the case of the cylindrical eccentric roundel 52, as shown in FIG. 32, the inclined top ring 58 is flatly attached to the bottom surface region of the piston operating zone 74 with respect to the diaphragm film 70. The component distribution of the force Fs is more linear, and therefore the slanting action is substantially eliminated by the relaxation of the compression phenomenon.

  Also, under the same acting force F, the reaction force Fs is inversely proportional to the contact area, so that the magnitude of the dispersion component of the reaction force Fs in the case of the cylindrical eccentric roundel 52 of the present invention is as shown in FIG. The magnitude of the dispersion component of the reaction force Fs in the case of the conventional tubular eccentric roundel 52 shown in FIG.

  The improvement in the linearity and the reduction in the magnitude of the distribution of the reaction force component Fs are obtained as a result of forming the inclined top ring 58 between the annular positioning groove 55 and the vertical side portion 56 in the eccentric roundel mount 50. Yes, and as a result, at least two effects can be obtained. First, this configuration facilitates breakage of the diaphragm membrane 70 due to the high frequency compression phenomenon caused by the presence of the round shoulder 57 on the horizontal top surface 53 except for the tubular eccentric roundel 52 in the conventional configuration. Is resolved. Second, the diaphragm membrane generated by the acting force F as a result of the sequential vertical displacement of the three piston operating zones 74 in the diaphragm membrane 70 driven by the vertical reciprocating stroke of the three tubular eccentric roundels or the cylindrical eccentric roundel 52. The reaction force Fs of 70 is significantly reduced.

As a result of these effects, the following benefits are obtained.
1. The durability of the diaphragm membrane 70 with respect to the sustained high frequency pumping operation of the cylindrical eccentric roundel 52 is greatly improved.
2. Less current is wasted as a result of the high frequency compression phenomenon, which significantly reduces the power consumption of the pressure diaphragm pump.
3. Due to the reduced power consumption, the operating temperature of the pressure diaphragm pump is significantly reduced.
4). Undesirable noise in the bearing due to the aging of the lubricant in the pumping diaphragm pump, usually accelerated by high operating temperatures, is largely eliminated.

The results of tests performed on the prototype of the present invention are as follows.
A. The service life of the tested diaphragm membrane 70 was more than twice.
B. The reduction in current consumption was over 1 amp.
C. The operating temperature decreased by more than 15 degrees Celsius.
D. The smoothness of the bearing has been improved.

  In a variation of the first exemplary embodiment, each of the base curved grooves 65 of the pump head body 60 can be adapted to a base curved hole 64 as shown in FIGS.

  As shown in FIGS. 36 and 37, in a first exemplary embodiment, each of the base curved grooves 65 in the pump head body 60 (as shown in FIGS. 20 and 22), and (as shown in FIGS. 24 and 25). The base curved protrusions 651 in the pump head body 60 (as shown in FIG. 36) can be formed on each of the corresponding base curved protrusions 77 in the diaphragm film 70 without affecting their fitting conditions (see FIG. 36). Can be exchanged for the corresponding base curved groove 771 in the diaphragm membrane 70).

  When the pump head body 60 and the diaphragm membrane 70 are assembled, each of the base curved protrusions 651 on the upper side of the pump head body 60 has a corresponding base curved groove on the bottom side of the diaphragm membrane 70 (as shown in FIG. 37). 771, and as a result, in the operation of the present invention as well (as shown in the enlarged portion of FIG. 37), the short moment arm length from the base curved groove 771 to the periphery of the annular positioning projection 76 in the diaphragm film 70 L3 is obtained, whereby the novel invention of the pump head main body 60 and the diaphragm membrane 70 has a remarkable effect in reducing vibration as well.

  Referring to FIGS. 38-44, which are illustrations of a multi-effect pumped diaphragm pump for the second exemplary embodiment of the present invention, a second outer curved groove 66 is further illustrated (shown in FIGS. 38-40). As shown) circumferentially disposed around each of the base curved grooves 65 in the pump head body 60, while a second outer curved projection 78 is further provided (as shown in FIGS. 42 and 43) diaphragm membrane 70. Are arranged circumferentially around each of the base curved projections 77 and at positions corresponding to the positions of the respective second outer curved grooves 66 for fitting in the pump head body 60.

  When the pump head body 60 and the diaphragm membrane 70 are assembled, each pair of the base curved projection 77 and the second outer curved projection 78 on the bottom side of the diaphragm membrane 70 (as shown in the enlarged portion of FIG. 44) , Fully inserted into each corresponding pair of base curved grooves 65 and second outer curved grooves 66 on the upper side of the pump head body 60, so that in the operation of the present invention (as shown in the enlarged portion of FIG. 44) A) A relatively short moment arm length L2 from the base curved projection 77 to the periphery of the annular positioning projection 76 in the diaphragm film 70 is obtained.

  The shortened moment arm length L2 not only shows a remarkable effect in vibration relaxation, but also has stability by preventing the displacement and maintaining the moment arm length L2 against the acting force F in the eccentric roundel 52. Increase.

  In the second exemplary embodiment, as shown in FIGS. 45 and 46, each pair of the base curved groove 65 and the second outer curved groove 66 of the pump head body 60 is connected to the base curved hole 64 and the second curved groove 64. A pair of outer curved holes 67 can be replaced.

  In a second exemplary embodiment, as shown in FIGS. 47 and 48, each pair of a base curved groove 65 and a second outer curved groove 66 in the pump head body 60 (as shown in FIGS. 38-40). , And each corresponding pair of base curved projections 77 and second outer curved projections 78 in diaphragm membrane 70 (as shown in FIGS. 42 and 43) without affecting their mating conditions (FIG. 47 (as shown in FIG. 47), a pair consisting of a base curved projection 651 and a second outer curved projection 661 in the pump head body 60, and a base curved groove 771 and a second outer curved shape in the diaphragm membrane 70 (as shown in FIG. 47). The corresponding pair of grooves 781 can be exchanged.

  When the pump head main body 60 and the diaphragm film 70 are assembled, each pair of the upper base curved protrusion 651 and the second outer curved protrusion 661 of the pump head main body 60 (as shown in FIG. 48) Of the base curved groove 771 and the second outer curved groove 781 on the bottom side of each of the diaphragms are completely inserted into the corresponding pairs, so that in the operation of the present invention (as shown in the enlarged portion of FIG. 48), the diaphragm membrane A short moment arm length L3 from the base curved groove 771 to the periphery of the annular positioning projection 76 in 70 is obtained, thereby realizing a significant relaxation of vibration and maintaining the moment arm length L2 while preventing displacement. Improve stability.

  49-55, which is an illustration of a multi-effect pumping diaphragm pump of a third exemplary embodiment of the present invention, further includes a base annular groove 601 (as shown in FIGS. 49-51). Around the operating holes 61 in the head body 60 are circumferentially arranged, while a base protrusion ring 701 is further provided (as shown in FIGS. 53 and 54) for each of the annular positioning protrusions 76 in the diaphragm film 70. It is arrange | positioned in the circumference | surroundings and the position corresponding to the position of each base annular groove 601 for fitting in the pump head main body 60 in the circumferential direction.

  During the assembly of the pump head body 60 and the diaphragm membrane 70, each of the base protrusion rings 701 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 55) has a corresponding base annular groove 601 on the upper side of the pump head body 60. As a result, in the operation of the present invention (as shown in FIG. 55), a short moment arm length L2 from the base projection ring 701 to the periphery of the annular positioning projection 76 in the diaphragm film 70 is obtained. Thus, the vibration is greatly reduced and the stability is improved by preventing the displacement against the acting force F in the eccentric roundel 52 and maintaining the moment arm length L2.

  In the third exemplary embodiment, as shown in FIGS. 56 and 57, each of the base annular grooves 601 of the pump head body 60 can be replaced with a base through hole 600.

  In a third exemplary embodiment, as shown in FIGS. 58 and 59, each of the base annular grooves 601 in the pump head body 60 (as shown in FIGS. 49-51), and (as shown in FIGS. 53 and 54). The base protrusion ring 610 in the pump head body 60 (as shown in FIG. 58) and each of the corresponding base protrusion rings 701 in the diaphragm membrane 70 without affecting their mating conditions (FIG. 58). Can be replaced with a corresponding base annular groove 710 in the diaphragm membrane 70 (as shown).

  During assembly of the pump head body 60 and diaphragm membrane 70, each of the base protrusion rings 610 on the upper side of the pump head body 60 has a corresponding base annular groove 710 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 59). As a result, a short moment arm length L3 from the base annular groove 710 in the diaphragm membrane 70 to the periphery of the annular positioning projection 76 is obtained in the operation of the present invention (as shown in FIG. 59). As a result, the novel invention of the pump head main body 60 and the diaphragm membrane 70 has a remarkable effect in reducing vibration.

  Referring to FIGS. 60-66, which are illustrations of a multi-effect pumped diaphragm pump of a fourth exemplary embodiment of the present invention, a further pair of curved concave segments 602 (as shown in FIGS. 60-62). ) Circumferentially disposed around each of the actuation holes 61 in the pump head body 60, while a further pair of curved convex segments 702 are provided as annular positioning protrusions in the diaphragm membrane 70 (as shown in FIGS. 64 and 65). Each of 76 is arranged in the circumferential direction and at a position corresponding to the position of each curved concave segment 602 for fitting in the pump head main body 60.

  During assembly of the pump head body 60 and the diaphragm membrane 70, each pair of curved convex segments 702 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 66) As a result, a short moment arm length L2 from the curved convex segment 702 to the periphery of the annular positioning projection 76 in the diaphragm membrane 70 is obtained in the operation of the present invention (as shown in FIG. 66). As a result, the vibration is greatly reduced and the stability is improved by preventing the displacement and maintaining the moment arm length L2.

  In the fourth exemplary embodiment, each pair of curved concave segments 602 of the pump head body 60 can be replaced with a pair of curved hole segments 611 as shown in FIGS.

  In a fourth exemplary embodiment, as shown in FIGS. 69 and 70, each pair of curved concave segments 602 in the pump head body 60 (as shown in FIGS. 60-62), and (shown in FIGS. 64 and 65). Each pair of curved convex segments 702 in diaphragm membrane 70 (as shown in FIG. 69) without affecting their mating conditions. And a corresponding pair of curved concave segments 720 in the diaphragm membrane 70 (as shown in FIG. 69) can be exchanged.

  During the assembly of the pump head body 60 and the diaphragm membrane 70, each pair of curved convex segments 620 on the upper side of the pump head body 60 is connected to the curved concave segment 720 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 70). As a result, a short moment arm length L3 from the curved concave segment 720 to the periphery of the annular positioning projection 76 in the diaphragm membrane 70 is also obtained (as shown in FIG. 70) in the operation of the present invention. As a result, the novel invention of the pump head body 60 and the diaphragm membrane 70 has a significant effect in reducing vibration.

  Referring to FIGS. 71-77, which are illustrations of a multi-effect pumping diaphragm pump of a fifth exemplary embodiment of the present invention, a further group of circular openings or holes 603 (as shown in FIGS. 71-73). D) are arranged circumferentially around each of the actuation holes 61 in the pump head body 60, while a further group of circular projections 703 (as shown in FIGS. 75 and 76) are annular positioning projections in the diaphragm membrane 70 Around 76, it is arrange | positioned in the circumferential direction and the position corresponding to the position of each group of the circular opening or hole 603 for fitting in the pump head main body 60. As shown in FIG.

  During the assembly of the pump head body 60 and the diaphragm membrane 70, each group of circular protrusions 703 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 77) As a result, a short moment arm length L2 from the circular protrusion 703 to the circumference of the annular positioning protrusion 76 in the diaphragm film 70 is obtained in the operation of the present invention (as shown in FIG. 77). As a result, the vibration is greatly reduced, and the stability is improved by preventing the displacement and maintaining the moment arm length L2.

  In the fifth exemplary embodiment, each group of circular openings or holes 603 in the pump head body 60 can be replaced with a group of circular through holes 612, as shown in FIGS.

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

  During the assembly of the pump head body 60 and the diaphragm membrane 70, each group of circular protrusions 630 on the upper side of the pump head body 60 (as shown in FIG. 81) is formed into circular openings or holes 730 on the bottom side of the diaphragm membrane 70. As a result, a short moment arm length L3 from the circular recess 730 to the periphery of the annular positioning protrusion 76 in the diaphragm film 70 is obtained in the operation of the present invention (as shown in FIG. 81). As a result, the novel invention of the pump head main body 60 and the diaphragm membrane 70 has a remarkable effect in the vibration reduction.

  Reference is made to FIGS. 82-88 which are illustrations of a sixth example embodiment multi-effect pumping diaphragm pump of the present invention.

  Further, a group of square openings or holes 604 are circumferentially disposed around each of the actuation holes 61 in the pump head body 60 (as shown in FIGS. 82-84), while a further group of square protrusions 704 are further present. (As shown in FIGS. 86 and 87) circumferentially around each of the annular positioning projections 76 in the diaphragm membrane 70 and corresponding to the position of each group of square openings or holes 604 for fitting in the pump head body 60. In place.

  During assembly of the pump head body 60 and the diaphragm membrane 70, each group of rectangular protrusions 704 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 88) As a result, a short moment arm length L2 from the square protrusion 704 to the periphery of the annular positioning protrusion 76 in the diaphragm film 70 is obtained in the operation of the present invention (as shown in FIG. 88). As a result, the vibration is greatly reduced, and the stability is improved by preventing the displacement and maintaining the moment arm length L2.

  In the sixth exemplary embodiment, each group of square openings or holes 604 in the pump head body 60 can be replaced with a group of square through holes 613, as shown in FIGS.

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

  During assembly of the pump head body 60 and the diaphragm membrane 70, each group of square projections 640 on the top side of the pump head body 60 (as shown in FIG. 92) is formed into a rectangular opening or hole 740 on the bottom side of the diaphragm membrane 70. Fully inserted into each corresponding group, so that also in the operation of the present invention (as shown in FIG. 92 and related enlarged views) a short moment from the square recess 740 to the periphery of the annular positioning projection 76 in the diaphragm membrane 70 The arm length L3 is obtained, whereby the novel invention for the pump head main body 60 and the diaphragm membrane 70 has a significant effect in reducing vibration.

  93-95, which are illustrations of a multi-effect pumping diaphragm pump of a seventh exemplary embodiment of the present invention, further concentric first inner annular groove 605 and second outer annular groove 606. Are arranged circumferentially around each of the actuation holes 61 in the pump head body 60 (as shown in FIG. 93), while being further concentric with the first inner projection ring 705 and the second A pair of outer projection rings 706 are circumferentially around each of the annular positioning projections 76 in the diaphragm membrane 70 (as shown in FIG. 94) and a first inner annular groove 605 for fitting in the pump head body 60. And the second outer annular groove 606 are arranged at positions corresponding to the respective positions.

  When the pump head body 60 and the diaphragm membrane 70 are assembled, each pair of the first inner projection ring 705 and the second outer projection ring 706 on the bottom side of the diaphragm membrane 70 (as shown in FIG. 95) Fully inserted into each corresponding pair of first inner annular groove 605 and second outer annular groove 606 on the upper side of pump head body 60, so that in the operation of the present invention (FIG. 95 and associated enlarged view). A short moment arm length L2 from the first inner protrusion ring 705 to the periphery of the annular positioning protrusion 76 in the diaphragm film 70 is obtained, thereby realizing vibration relaxation and acting on the eccentric roundel 52. The stability in the moment arm length L2 is improved against the force F.

  In the seventh exemplary embodiment, as shown in FIGS. 96 and 97, each pair of concentric first inner annular groove 605 and second outer annular groove 606 in the pump head body 60 is concentrically connected. A pair of one inner hole ring 614 and second outer hole ring 615 can be substituted.

  In a seventh exemplary embodiment, as shown in FIGS. 98 and 99, from concentric first inner annular groove 605 and second outer annular groove 606 in pump head body 60 (as shown in FIG. 93). And the corresponding pair of concentric first inner protrusion ring 705 and second outer protrusion ring 706 in diaphragm membrane 70 (as shown in FIG. 94) affect their mating conditions. Without effect, a pair of concentric first inner protrusion ring 650 and second outer protrusion ring 660 in pump head body 60 (as shown in FIG. 98) and diaphragm membrane 70 (as shown in FIG. 98). The corresponding pairs of concentric first inner annular groove 750 and second outer annular groove 760 can be exchanged.

  When the pump head body 60 and the diaphragm membrane 70 are assembled, each pair of the first inner protrusion ring 650 and the second outer protrusion ring 660 on the upper side of the pump head body 60 (as shown in FIG. 99) Fully inserted into each corresponding pair of first inner annular groove 750 and second outer annular groove 760 on the bottom side of diaphragm membrane 70, so that also in the operation of the present invention (as shown in FIG. 99) ) A short moment arm length L3 from the first inner annular groove 750 to the periphery of the individual annular positioning projections 76 in the diaphragm film 70 is obtained, thereby realizing a significant relaxation of vibrations and preventing a displacement. Stability is improved by maintaining the arm length L2.

  Reference is made to FIGS. 100-102, which are illustrations of a multi-effect pump diaphragm pump of a variation of the eighth exemplary embodiment of the present invention.

  In this modification, the cylindrical eccentric roundel 52 is changed to an inverted frustoconical eccentric roundel 502 in the eccentric roundel mount 500.

  The frustoconical eccentric roundel 502 has an integral inverted frustoconical side 506 and an inclined top ring 508. Although the outer diameter of the frustoconical eccentric roundel 502 is enlarged, it still remains in the pump head body 60. The inclined top ring 508 is smaller than the inner diameter of the operating hole 61 and extends between the annular positioning groove 505 and the inverted frustoconical side portion 506.

  103 to 105 are explanatory views showing a changed operation of the “multi-effect pressure-feeding diaphragm pump” in the eighth exemplary embodiment of the present invention.

  First, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11 so that the three frustoconical eccentric roundels 502 on the eccentric roundel mount 50 are continuously and sequentially. Operates up and down reciprocating stroke.

  Secondly, the three piston operation zones 74 in the diaphragm membrane 70 are moved up and down by being sequentially driven by the up and down reciprocating strokes of the three frustoconical eccentric roundels 502.

  Third, when the frustoconical eccentric roundel 502 according to the present invention performs an upward stroke operation to displace the piston operation zone 74 upward, the corresponding force F causes the corresponding annular positioning projections 76 of the diaphragm film 70 and the outer side of the piston to move outward. A portion between the rising rim 71 and the rising rim 71 is partially pulled obliquely.

  As a result, including an inclined top ring 508 in the eccentric roundel mount 500 would otherwise cause high frequency compression as a result of the round shoulder 57 of the conventional tubular eccentric roundel 502 (as shown by the dotted line in FIG. 105). The breakage of the diaphragm film 70 caused by the phenomenon is eliminated, and the reaction force Fs of the diaphragm film 70 caused by the acting force F is significantly reduced. On the other hand, despite the fact that the outer diameter of the frustoconical eccentric roundel 502 is enlarged, the frustoconical eccentric roundel 502 can collide with the operation hole 61 in the pump head body 60 by the inverted frustoconical side portion 506. Sex is excluded.

  Under the same acting force F, the reaction force Fs is inversely proportional to the contact area. In the case of the inverted frustoconical eccentric roundel 502 of the present invention, due to the enlarged outer diameter of the inverted frustoconical eccentric roundel 502 (as shown by ring A in FIG. 105), the inclined top ring 508 and the bottom of the diaphragm membrane 70 The contact area with the side is increased, so that all dispersion components of the reaction force Fs are further reduced.

Therefore, at least a part of the following effects can be obtained by the inverted frustoconical eccentric roundel 502 of the present embodiment of the present invention.
1. As a result of the inverted frustoconical eccentric roundel 502, the durability of the diaphragm membrane 70 for sustained high frequency pumping operations is greatly improved.
2. Less current is wasted as a result of the high frequency compression phenomenon, which significantly reduces the power consumption of the pressure diaphragm pump.
3. Due to the reduced power consumption, the operating temperature of the pressure diaphragm pump is significantly reduced.
4). The undesirable noise of the bearing due to the aging of the lubricant in the pumping diaphragm pump, which is exacerbated by premature aging due to high operating temperatures, is largely eliminated.
5. In the case of the inverted frustoconical eccentric roundel 502 of the present invention, the service life of the pumping diaphragm pump is further extended by reducing all the dispersion components of the reaction force Fs.

  FIGS. 106-109 are illustrations showing the adaptation of the multi-effect pumped diaphragm pump in the eighth exemplary embodiment of the present invention, where the cylindrical eccentric roundel 52 is in the eccentric roundel mount 500. It is replaced by a combination eccentric roundel 502. The combined eccentric roundel 502 has a roundel mount 511 and a removably separated inverted frustoconical roundel yoke 521, and the outer diameter of the frustoconical roundel yoke 521 is enlarged, but still remains the pump head body 60. The roundel mount 511 has two layers including a lower layer base 512 having an inwardly facing meniscus and an upper layer protruding cylinder 513 having a female screw hole 514 at the center. The inverted frustoconical roundel yoke 521 is mounted on the corresponding roundel mount 511 in a sleeve shape, and has an upper hole 523, an intermediate hole 524, and a lower hole stacked as a three-layered integral hollow frustoconical structure. It has a hole 525, an inverted frustoconical side portion 522, and an inclined top ring 526 that extends from the upper hole 523 to the inverse frustoconical side portion 522. The inner diameter of the upper hole 523 is larger than the outer diameter of the protruding cylinder 513. The inner diameter of the middle hole 524 is substantially equal to the outer diameter of the protruding cylinder 513, the inner diameter of the lower hole 525 is substantially equal to the outer diameter of the lower layer base in the roundel mount 511, By engaging the corresponding surface of the pilot hole, the relative rotation of the roundel mount 511 corresponding to the roundel yoke 521 is prevented. When the frustoconical roundel yoke 521 is mounted in a sleeve shape on the roundel mount 511 (as shown in FIGS. 108 and 109), a positioning annular groove 515 is formed between the protruding cylinder 513 and the inner wall of the upper hole 523. Is formed.

  FIGS. 110 and 113 illustrate a method of assembling a multi-effect pumped diaphragm pump according to the above adaptation of the eighth exemplary embodiment of the present invention.

  First, the frustoconical roundel yoke 521 is fitted on the roundel mount 511.

  Second, all three annular positioning projections 76 of diaphragm membrane 70 are inserted into three corresponding positioning annular grooves 515 in three combined eccentric roundels 502 of eccentric roundel mount 500.

  Finally, after each fastening screw 1 is inserted into the corresponding stepped hole 81 of the pumping piston 80 and each corresponding working zone hole 75 in the piston working zone 74 of the diaphragm membrane 70, the fastening screw 1 is eccentric. The diaphragm membrane 70 and the three pumping pistons 80 are assembled and fixed (as shown in FIG. 110) by screwing them into the three corresponding female screw holes 514 in the three roundel mounts 511 of the roundel mount 500.

  111 and 113 illustrate the operation of a multi-effect pressure-feeding diaphragm pump according to the above adaptation of the eighth exemplary embodiment of the present invention.

  First, when the motor 10 is powered on, the wobble plate 40 is rotationally driven by the motor output shaft 11, so that the three combined eccentric roundels 502 on the eccentric roundel mount 50 are continuously reciprocated up and down. Stroke operation.

  Secondly, the three piston operating zones 74 in the diaphragm membrane 70 are sequentially driven by the up and down reciprocating strokes of the three combined eccentric roundels 502 so as to move up and down.

  Third, when the combined eccentric roundel 502 in the present invention performs an upward stroke operation and the piston operating zone 74 is displaced upward, the corresponding annular positioning protrusion 76 of the diaphragm film 70 and the outer rising rim are caused by the acting force F. The part between 71 will be pulled partially diagonally.

  As a result, including an inclined top ring 526 in the inverted frustoconical roundel yoke 521 of the eccentric roundel mount 500 results in a high as a result of the conventional tubular eccentric roundel shoulder 57 shown otherwise in dotted lines in FIG. The ease of breakage of the diaphragm film 70 caused by the frequency compression phenomenon is eliminated, and the reaction force Fs of the diaphragm film 70 generated by the acting force F (as shown in FIG. 112) is remarkably reduced. .

  Under the same acting force F, the reaction force Fs is inversely proportional to the contact area. In the case of the inverted frustoconical roundel yoke 521 of the present invention, due to the enlarged outer diameter of the inverted frustoconical roundel yoke 521 (as shown by ring A in FIG. 113), the bottom of the inclined top ring 508 and the diaphragm membrane 70. The contact area with the side is increased, so that all dispersion components of the reaction force Fs are further reduced.

  The manufacture of a multi-effect pumped diaphragm pump by this adaptation of the eighth exemplary embodiment of the present invention is as follows.

  First, the roundel mount 511 and the eccentric roundel mount 500 are manufactured together.

  Second, the frustoconical roundel yoke 521 is manufactured independently as a separate body.

  Finally, the frustoconical roundel yoke 521 and the integral roundel mount 511, together with the eccentric roundel mount 500, are assembled into an integral assembly to produce the assembled eccentric best shown in FIGS. Roundel 502 is formed.

  Thereby, the invention of the combined eccentric roundel 502 not only satisfies the requirements of mass production, but also reduces the overall manufacturing cost.

The eccentric roundel 502 having the frustoconical roundel yoke 521 of the present invention provides at least a part of the following effects.
1. By including the inverted frustoconical roundel yoke 521, the durability of the diaphragm membrane 70 for sustained high frequency pumping operations is greatly improved.
2. Less current is wasted as a result of the high frequency compression phenomenon, which significantly reduces the power consumption of the pressure diaphragm pump.
3. Due to the reduced power consumption, the operating temperature of the pressure diaphragm pump is significantly reduced.
4). Undesirable noise in the bearing as a result of lubricant temperature-accelerated aging in the pumped diaphragm pump is largely eliminated.
5. In the case of the inverted frustoconical roundel yoke 521 of the present invention, the service life of the pressure-feeding diaphragm pump is further extended by further reducing all the dispersion components of the reaction force Fs.
6). Since the present invention is suitable for mass production, the manufacturing cost of the pressure diaphragm pump is reduced.

  As described above, the present invention realizes a significant vibration reduction effect in the pressure-feeding diaphragm pump without increasing the overall cost by a simple new fitting means for the pump head body and the diaphragm membrane, As a result, all the problems of noise and resonance vibration due to vibration generated in the conventional pumping diaphragm pump are solved. Furthermore, the simple inclined top ring of the various cylindrical eccentric roundels of the present invention can double the useful life of the diaphragm membrane in a pumped diaphragm pump, which is useful with respect to industrial applicability.

Claims (20)

A multi-effect pressure-feeding diaphragm pump, comprising a motor, a pump head body fixed to the motor housing, a roundel mount disposed below the pump head body, and a top surface and a fastening hole formed in the top surface the possess respectively, comprises a Raunderu plurality of eccentricity is eccentric with respect to the output shaft of the motor, the eccentric Raunderu is the Raunderu mount to extend through the operation hole in the pump head body The diaphragm membrane is fixed to the eccentric roundel through the operation hole, and is disposed on the upper side of the pump head body, and a plurality of pumping pistons are pumped when the diaphragm membrane is operated. In a pumping diaphragm pump configured to move,
The roundel mount is disposed on a wobble plate, and the wobble plate is rotated by the motor to swing the roundel mount. As a result, the eccentric roundel moves up and down sequentially, The pumping piston reciprocates in sequence by the up and down movement of the eccentric roundel,
The pump head body has at least one first curved vibration damping positioning structure in each operation hole on the upper side of the pump head body,
The diaphragm membrane has at least one second curved positioning structure at each position on the diaphragm membrane corresponding to the position of the at least one first damping positioning structure in the pump head body;
Wherein the at least one first positioning structure is to mate with the at least one second positioning structure corresponding,
The diaphragm membrane further comprises a plurality of annular flanges configured to mate with individual annular positioning grooves on the top surface of each of the eccentric roundels,
The peripheral edge of the top surface of each eccentric roundel is inclined with respect to the central plane , and the inclined top ring is inclined between each of the annular positioning grooves of each individual eccentric roundel and the vertical side or the inverted frustoconical side. By improving the linearity of the component distribution of the reaction force of the diaphragm membrane that occurs when an acting force acts during the operation of the diaphragm pump ,
Each of the eccentric roundels has an inverted frustoconical shape, and the maximum diameter of the eccentric roundel is smaller than the inner diameter of the corresponding one of the operating holes in the pump head body,
Each of the eccentric roundels has a mounting portion fixed to the roundel mount and a separable inverted frustoconical roundel yoke attached to the roundel mount, thereby providing a two-layer eccentric roundel structure. A multi-effect pressure-feeding diaphragm pump that is formed . The motor has an output shaft, the wobble plate has a cam lobe shaft that projects integrally, and a piston valve assembly;
The output shaft of the motor extends through a shaft coupling hole in the wobble plate to rotate the wobble plate,
The cam lobe with a shaft which projects to the integral of the wobble plate, extends through the center bearing of the Raunderu mount,
Position the pump head body is fixed to the upper chassis of the motor surrounds the wobble plate and said Raunderu mount therein, said pump head body, corresponding to the position of the plurality of eccentric Raunderu A plurality of said operating holes, each of which is slightly larger than an outer diameter of a corresponding one of said eccentric roundels to receive a corresponding one of said eccentric roundels, respectively. Has an inner diameter,
The diaphragm membrane is made of an elastic material and is disposed on the pump head body, and the diaphragm membrane has at least one rising rim and is connected to the at least one rising rim at equal intervals. A plurality of spaced apart radial rising partition ribs, thereby forming equivalent piston operating zones, each piston operating zone having an operating zone hole formed therein, each of the eccentric roundels; At a position corresponding to the position of the fastening hole in
Each pumping piston has a stepped hole, and a fastening member passes through the stepped hole of each pumping piston and the corresponding working zone hole of each piston operating zone in the diaphragm membrane for each individual eccentric roundel. said by extending fastening hole, the pumping piston of the diaphragm membrane and each is fixed to the eccentric Raunderu corresponding in the Raunderu mount,
The piston valve assembly covers the diaphragm membrane and is fixed around the diaphragm membrane by a sealing engagement and has a central outlet mount with a central positioning hole and a plurality of equivalent sectors; Each of the sectors includes a plurality of outlet ports equally spaced in the circumferential direction, and the piston valve assembly further includes a T-type plastic backflow check valve with a central positioning shank, and a plurality of inlet mounts in the circumferential direction. Each of the inlet mounts has a plurality of inlet ports equally spaced in the circumferential direction, and an inverted central piston disk attached to each of the inlet mounts, whereby each piston disk has a plurality of The central positioning shaft of the plastic backflow prevention valve. And the plurality of outlet ports in the central circular outlet mount communicate with the plurality of inlet mounts, and the diaphragm membrane is disposed around the periphery of the central outlet mount. When secured to the piston valve assembly, a sealed pre-hydraulic chamber is formed in each inlet mount and a corresponding piston actuation zone in the diaphragm membrane, and one end of each of the pre-hydraulic chambers is connected to the inlet port. Can communicate with the corresponding one of
A pump head cover covers the pump head body and surrounds the piston valve assembly, the pumping piston, and the diaphragm membrane, and has a water inlet orifice and a water outlet orifice, A head cover is hermetically attached to an assembly comprising the diaphragm membrane and the piston valve assembly, and a high water pressure chamber is formed between a cavity formed by an inner wall of an annular rib ring and the central outlet mount of the piston valve assembly. The multi-effect pressure-feeding diaphragm pump according to claim 1. The at least one first positioning structure includes at least one of a base curved groove, a curved slot, a curved opening group, a curved projection, and a curved projection group, and each of the operation holes in the pump head body. It is arranged in the circumferential direction around the upper side,
The at least one second vibration damping positioning structure has one of a base curved projection, a curved projection group, a curved groove, a curved slot, and a curved opening group, and each of the bottom side of the diaphragm membrane In the circumferential direction around the concentric annular positioning protrusion, and at a position corresponding to the position of each first positioning structure in the pump head body, when assembling the pump head body and the diaphragm membrane, 2. The multi-effect pressure-feeding diaphragm pump according to claim 1, wherein each second positioning structure on the bottom side of the diaphragm membrane is fitted with each corresponding first positioning structure on the upper side of the pump head body.   Each of the first damping and positioning structures has at least one curved groove or slot in the pump head body, and each of the second damping and positioning structures has at least one extending from the diaphragm membrane. The multi-effect pressure-feeding diaphragm pump according to claim 1, having a curved projection.   Each of the first vibration damping positioning structures has at least one curved protrusion extending from the pump head body, and each of the second vibration damping positioning structures has at least one curved groove in the diaphragm membrane. The multi-effect pressure-feeding diaphragm pump according to claim 1, further comprising a slot.   Each of the first vibration damping positioning structures has a pair of curved grooves in the pump head body, and each of the second vibration damping positioning structures has a pair of curved protrusions extending from the diaphragm film. The multi-effect type pressure-feeding diaphragm pump according to claim 1.   Each of the first vibration damping positioning structures has a pair of curved protrusions extending from the pump head body, and each of the second vibration damping positioning structures has a pair of curved grooves in the diaphragm membrane. The multi-effect type pressure-feeding diaphragm pump according to claim 1.   Each of the first vibration damping positioning structures is a group of curved openings in the pump head body, and each of the second vibration damping positioning structures is a group of curved protrusions extending from the diaphragm film. The multi-effect pressure-feeding diaphragm pump according to claim 1.   The multi-effect pressure-feeding diaphragm pump according to claim 8, wherein the opening is a circular or square opening.   Each of the first vibration damping positioning structures is a group of curved protrusions extending from the pump head body, and each of the second vibration damping positioning structures is a group of curved openings in the diaphragm membrane. The multi-effect pressure-feeding diaphragm pump according to claim 1.   The multi-effect pressure-feeding diaphragm pump according to claim 10, wherein the protrusion is a circular or square protrusion.   Each of the first vibration damping positioning structures has at least one concave ring in the pump head body, and each of the second vibration damping positioning structures has at least one annular protrusion protruding from the diaphragm membrane. The multi-effect pressure-feeding diaphragm pump according to claim 1, comprising:   Each of the first vibration damping positioning structures has a pair of concave rings in the pump head body, and each of the second vibration damping positioning structures has a pair of ring structures protruding from the diaphragm membrane, The multi-effect pressure-feeding diaphragm pump according to claim 1.   Each of the first damping positioning structures has a pair of ring structures protruding from the pump head body, and each of the second damping positioning structures has a pair of concave rings in the diaphragm membrane, The multi-effect pressure-feeding diaphragm pump according to claim 1. The attachment portion of each of the eccentric Raunderu, the a Raunderu mount integral with the the inverted truncated cone-shaped round del yoke are separate, multiple-effect type pumping diaphragm pump according to claim 1. The attachment portion of each of the eccentric Raunderu has base with a positioning surface inward, and a cylinder having a female screw hole in the center extends upwardly from said base, said inverted truncated cone shape Raunderu yoke Each has an upper hole, a middle hole, and a lower hole, and the diameter of the middle hole is substantially equal to the diameter of the cylinder of the mounting portion, and the diameter of the upper hole is larger than the diameter of the cylinder of the mounting portion. The diameter of the lower hole is substantially equal to the diameter of the base of the mounting portion, the lower hole is externally fitted to the base, the inner hole is mounted in a sleeve shape on the cylinder, and the annular positioning groove is The multi-effect pressure-feeding diaphragm pump according to claim 1, defined by a space between the cylinder and the inner wall of the upper hole. 3. The multi-effect pressure-feeding diaphragm pump according to claim 2 , wherein the number of each of the eccentric roundel, the operation hole in the pump head body, the piston operation zone, and the pumping piston is three.   The at least one rising rim of the diaphragm membrane is an inner rising rim, the diaphragm membrane has a parallel outer rising rim, and the piston valve assembly has a rising rim extending downwardly. When the diaphragm membrane is fixed to the piston valve assembly at the periphery, the rising rim extending downward of the piston valve assembly extends between the inner and outer rising rims of the diaphragm membrane. The multi-effect pressure-feeding diaphragm pump according to claim 2, which provides a peripheral seal.   The multi-effect pressure-feeding diaphragm pump according to claim 1, wherein the motor is a brush motor.   The multi-effect pressure-feeding diaphragm pump according to claim 1, wherein the motor is a brushless motor.