Patent Grant
9945372
The present invention relates to a compressing diaphragm pump with multiple effects used in a reverse osmosis (RO) purification system, and particularly to a compressing diaphragm pump having an innovative mating means for the pump head body and diaphragm membrane to reduce unwanted noise and shaking caused by resonant vibrations in the conventional compressing diaphragm pump, as well as a sloped top ring in the eccentric roundel mount that can eliminate the oblique pulling and squeezing phenomena of the pump so that the service lifespan of the compressing diaphragm pump and the durability of key components therein are prolonged.
Conventional compressing diaphragm pumps of the type commonly used with RO (Reverse Osmosis) purifier or RO water purification systems are disclosed in U.S. Pat. Nos. 4,396,357, 4,610,605, 5,476,367, 5,571,000, 5,615,597, 5,649,812, 5,706,715, 5,791,882 and 5,816,133. An example of a conventional compressing diaphragm pump is shown in
The motor upper chassis 30 includes a bearing 31 through which an output shaft 11 of the motor 10 extends. The motor upper chassis 30 also includes an upper annular rib ring 32 with several fastening bores 33 evenly and circumferentially disposed in a rim of the upper annular rib ring 32
The wobble plate 40 includes a shaft coupling hole 41 through which the corresponding motor output shaft 11 of the motor 10 extends.
The eccentric roundel mount 50 includes a central bearing 51 at the bottom thereof for receiving the corresponding wobble plate 40. Three tubular eccentric roundels 52 are evenly and circumferentially disposed on the eccentric roundel mount 50. Each tubular eccentric roundel 52 has a horizontal top face 53, a female-threaded bore 54 and an annular positioning groove 55 formed in the top face thereof, as well as a rounded shoulder 57 created at the intersection of the horizontal top face 53 and a vertical flank 56.
The pump head body 60 covers the upper annular rib ring 32 of the motor upper chassis 30 to encompass the wobble plate 40 and eccentric roundel mount 50 therein, and includes three operating holes 61 evenly and circumferentially disposed therein. Each operating hole 61 has an inner diameter that is slightly bigger than the outer diameter of the corresponding tubular eccentric roundel 52 in the eccentric roundel mount 50 for receiving each corresponding tubular eccentric roundel 52 respectively, a lower annular flange 62 formed thereunder for mating with corresponding upper annular rib ring 32 of the motor upper chassis 30, and several fastening bores 63 evenly disposed around a circumference of the pump head body 60.
The diaphragm membrane 70, which is extrusion-molded from a semi-rigid elastic material and placed on the pump head body 60, includes a pair of parallel rims, including outer raised rim 71 and inner raised rim 72, as well as three evenly spaced radial raised partition ribs 73 such that each end of radial raised partition ribs 73 connects with the inner raised rim 72, thereby forming three equivalent piston acting zones 74 within and partitioned by the radial raised partition ribs 73, wherein each piston acting zone 74 has an acting zone hole 75 created therein in correspondence with a respective female-threaded bore 54 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, and an annular positioning protrusion 76 for each acting zone hole 75 is formed at the bottom side of the diaphragm membrane 70 (as shown in
Each pumping piston 80, which is respectively disposed in each corresponding piston acting zones 74 of the diaphragm membrane 70, has a tiered hole 81 extending therethrough. After each of the annular positioning protrusions 76 in the diaphragm membrane 70 have been inserted into a corresponding annular positioning dent 55 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, respective fastening screws 1 are inserted through the tiered hole 81 of each pumping piston 80 and the acting zone hole 75 of each corresponding piston acting zone 74 in the diaphragm membrane 70, so that the diaphragm membrane 70 and three pumping pistons 80 can be securely screwed into female-threaded bores 54 of the corresponding three tubular eccentric roundels 52 in the eccentric roundel mount 50 (as can be seen in the enlarged portion of
Piston valvular assembly 90 covers the diaphragm membrane 70 and includes a downwardly extending raised rim 91 for insertion into the gap ring between the outer raised rim 71 and inner raised rim 72 in the diaphragm membrane 70, a central dish-shaped round outlet mount 92 having a central positioning bore 93 with three equivalent sectors, each of which contains multiple evenly circumferentially-located outlet ports 95, a T-shaped plastic anti-backflow valve 94 with a central positioning shank, and three circumferentially-adjacent inlet mounts 96. Each of the circumferentially-adjacent inlet mounts 96 includes multiple evenly circumferentially-located inlet ports 97 and an inverted central piston disk 98 respectively so that each piston disk 98 serves as a valve for each corresponding group of multiple inlet ports 97. The central positioning shank of the plastic anti-backflow valve 94 mates with the central positioning bore 93 of the central outlet mount 92 such that multiple outlet ports 95 in the central round outlet mount 92 are in communication with the three inlet mounts 96, and a hermetically sealed preliminary-compression chamber 26 is formed between each inlet mount 96 and a corresponding piston acting zone 74 in the diaphragm membrane 70 upon insertion of the downwardly extending raised rim 91 into the gap ring between the outer raised rim 71 and inner raised rim 72 of diaphragm membrane 70, such that one end of each preliminary-compressing chamber 26 is in communication with each of the corresponding inlet ports 97 (as shown in the enlarged portion of
The pump head cover 20, which covers the pump head body 60 to encompass the piston valvular assembly 90, pumping piston 80 and diaphragm membrane 70 therein, includes a water inlet orifice 21, a water outlet orifice 22, and several fastening bores 23. A tiered rim 24 and an annular rib ring 25 are disposed in the bottom inside of the pump head cover 20 such that the outer rim for the assembly of diaphragm membrane 70 and piston valvular assembly 90 can be hermetically attached to the tiered rim 24 (as shown in the enlarged portion of
By running each fastening bolt 2 through a corresponding fastening bore 23 of pump head cover 20 and a corresponding fastening bore 63 in the pump head body 60, and then putting a nut 3 onto each fastening bolt 2 to securely screw the pump head cover 20 to the pump head body 60 via the corresponding fastening bores 33 in the motor upper chassis 30, the whole assembly of the compressing diaphragm pump is finished (as shown in
Please refer to
Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three tubular eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.
Secondly, in the meantime, the three pumping pistons 80 and three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels 52 to move in an up-and-down displacement.
Thirdly, when the tubular eccentric roundel 52 moves in a down stroke, causing pumping piston 80 and piston acting zone 74 to be displaced downwardly, the piston disk 98 in the piston valvular assembly 90 is pushed into an open status so that tap water W can flow into the preliminary-compression chamber 26 via water inlet orifice 21 in the pump head cover 20 and inlet ports 97 in the piston valvular assembly 90 (as indicated by the arrowhead extending from W in the enlarged view of
Fourthly, when the tubular eccentric roundel 52 moves in an up stroke, causing pumping piston 80 and piston acting zone 74 to be displaced upwardly, the piston disk 96 in the piston valvular assembly 90 is pulled into a closed status to compress the tap water W in the preliminary-compression chamber 26 and increase the water pressure therein up to a range of 80 psi-100 psi. The resulting pressurized water Wp causes the plastic anti-backflow valve 94 in the piston valvular assembly 90 to be pushed to an open status.
Fifthly, when the plastic anti-backflow valve 94 in the piston valvular assembly 90 is pushed to an open status, the pressurized water Wp in the preliminary-compression chamber 26 is directed into high-compression chamber 27 via the group of outlet ports 95 for the corresponding sector in the central outlet mount 92, and then expelled out of the water outlet orifice 22 in the pump head cover 20 (as indicated by arrowhead W in the enlarged portion of
Finally, the sequential iterative action for each group of outlet ports 95 for the three sectors in central outlet mount 92 causes the pressurized water Wp to be constantly discharged out of the conventional compressing diaphragm pump to be further RO-filtered by the RO-cartridge so that the final filtered pressurized water Wp can be used in the reverse osmosis water purification system.
Referring to
To address the drawbacks of the conventional compressing diaphragm pump, as shown in
In addition to drawback of increasing overall vibration noise of the housing C, a further drawback occurs in that the water pipe P connected to the water outlet orifice 22 of the pump head cover 20 will synchronously shake in resonance with the vibrations described above (as indicated by the broken line depictions of water pipe P in
Meanwhile a corresponding plurality of rebounding forces Fs are created in reaction to the acting force F exerted on the bottom side of diaphragm membrane 70, with different components distributed over the entire bottom area of each corresponding piston acting zone 74 in the diaphragm membrane 70, as shown in
Among all of the distributed components of the rebounding force Fs, the maximum component force is exerted at the contacting bottom position P of the diaphragm membrane 70 with the rounded shoulder 57 of the horizontal top face 53 in the tubular eccentric roundel 52 so that the squeezing phenomenon at the bottom position P is also maximum, as shown in
With the rotational speed for the motor output shaft 11 of the motor 10 reaching a range of 700-1200 rpm, each bottom position P of the piston acting zone 74 of the diaphragm membrane 70 suffers from the squeezing phenomenon at a frequency of four times per second. Under such circumstances, the bottom position P of the diaphragm membrane 70 is always the first broken place for the entire conventional compressing diaphragm pump, which is an essential cause of not only shortening the service lifespan but also terminating the normal function of the conventional compressing diaphragm pump.
Therefore, how to substantially reduce the drawbacks associated with the squeezing phenomenon caused by the constant application of force F to the bottom side of each piston acting zone 74 of the diaphragm membrane 70 as a result of the movement of the tubular eccentric roundel 52 has also become an urgent and critical issue.
An objective of the present invention is to provide a compressing diaphragm pump with multiple effects, including an innovative mating means for a pump head body and a diaphragm membrane, in which the pump head body includes three operating holes and a basic curved groove, slot, or perforated segment, or a curved protrusion or set of protrusions, at least partially circumferentially-disposed around the upper side of each operating hole while the diaphragm membrane includes three equivalent piston acting zones, each of which has an acting zone hole, an annular positioning protrusion for each acting zone hole, and a basic curved protrusion or set of protrusions, or a groove, slot, or perforated segment, at least partially circumferentially-disposed around each concentric annular positioning protrusion at a position corresponding to the position of a corresponding mating basic curved groove, slot, or perforated segment, or curved protrusion or set of protrusions, in the pump head body, so that the three basic curved protrusions, sets of protrusions, grooves, slots, or perforated segments are completely inserted into or received by the corresponding three basic curved grooves, slots, perforated segments, protrusions, or sets of protrusions in the pump heat body with a short length of moment arm to generate less torque, the torque being obtained by multiplying the length of the moment arm by a constant acting force. With less torque, the vibration strength of the compressing diaphragm pump is substantially reduced.
Another objective is to provide a compressing diaphragm pump with multiple effects, including an innovative mating means for a pump head body and a diaphragm membrane, in which the pump head body has three basic curved grooves, slots, or perforated segments, or curved protrusions or set of protrusions, and the diaphragm membrane has three basic curved protrusions or sets of protrusions, or grooves, slots, or perforated segments, such that three basic curved protrusions or sets of protrusions, or grooves, slots, or perforated segments are completely inserted into or received by the corresponding three basic curved grooves, slots, or perforated segments, or curved protrusions or set of protrusions, with a short length of moment arm that generates less torque, the torque being obtained by multiplying the length of the moment arm by a constant acting force. With less torque, the vibration strength of the compressing diaphragm pump is substantially reduced. When the present invention is installed on the housing of a reverse osmosis purification unit of a water supplying apparatus in either a house or mobile home and cushioned by a conventional cushion base with a rubber shock absorber, the annoying noise caused by resonant shaking that occurred in the conventional compressing diaphragm pump can be completely eliminated.
A further object of the present invention is to provide a compressing diaphragm pump with multiple effects, which includes a cylindrical eccentric roundel disposed in an eccentric roundel mount. The cylindrical eccentric roundel includes an annular positioning groove, a vertical flank and an annular top surface portion that is inclined relative to horizontal to form a sloped top ring between the annular positioning groove and the vertical flank. By means of the sloped top ring, the high-frequency oblique pulling and squeezing phenomena that occurs in a conventional tubular eccentric roundel are completely eliminated because the sloped top ring flatly attaches the bottom area of corresponding piston acting zone for the diaphragm membrane. Thus, not only is the durability of the diaphragm membrane enhanced to better withstand the sustained high-frequency pumping action of the eccentric roundels, but the service lifespan of the diaphragm membrane is also greatly prolonged.
Yet another objective of the present invention is to provide a compressing diaphragm pump with multiple effects, which includes a cylindrical eccentric roundel disposed in an eccentric roundel mount. The cylindrical eccentric roundel includes an annular positioning groove, a vertical flank and a sloped top ring formed between the annular positioning groove and the vertical flank. By means of the sloped top ring, all distributed components of the rebounding force for the cylindrical eccentric roundels that are generated in reaction to the acting force caused by the pumping action are substantially reduced because the sloped top ring flatly attaches to the bottom area of the corresponding piston acting zone for the diaphragm membrane.
In achieving the above-described objectives, which are not intended to be limiting, at least the following benefits are obtained:
1. The durability of the diaphragm membrane for sustaining the high-frequency pumping action of the cylindrical eccentric roundels is substantially enhanced.
2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the above-described high-frequency squeezing phenomena.
3. The working temperature of the compressing diaphragm pump is tremendously reduced due to less power consumption.
4. The annoying noise of the bearings that results from aged lubricant in the compressing diaphragm pump, which is expeditiously accelerated by the high working temperature, is mostly eliminated.
A basic curved groove 65 is circumferentially disposed around the upper side of each operating hole 61 in the pump head body 60 while a basic curved protrusion 77 is circumferentially disposed around each concentric annular positioning protrusion 76 at the bottom side of the diaphragm membrane 70 at a position corresponding to the position of each mating basic curved groove 65 in the pump head body 60.
Thereby, each basic curved protrusions 77 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding basic curved groove 65 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Moreover, the cylindrical eccentric roundel 52 in the eccentric roundel mount 50 includes an annular top surface portion that is inclined relative to horizontal to form a sloped top ring 58 between the annular positioning groove 55 and a vertical flank 56, the sloped top ring 58 replacing the conventional rounded shoulder 57 in each tubular eccentric roundel 52 of the eccentric roundel mount 50 (as shown in
During operation of a conventional compressing diaphragm pump, a length of moment arm L1 from the outer raised rim 71 to the periphery of the annular positioning protruding block 76 in the diaphragm membrane 70 is obtained, as shown in
Because the resultant torque is calculated by same acting force F multiplying the length of moment arm, the resultant torque of the present invention is smaller than that of the conventional compressing diaphragm pump since the length of moment arm L2 is shorter than the length of moment arm L1. With the smaller resultant torque of the present invention, the vibration strength related resulting therefrom is substantially reduced.
In a practical test of a prototype of the present invention, the vibration strength was reduce to only one tenth (10%) of the vibration strength in the conventional compressing diaphragm pump.
If the present invention is installed on the housing C of a reverse osmosis purification unit cushioned by a conventional cushion base 100 with a rubber shock absorber 102, as shown in
Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three cylindrical eccentric roundels 52 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.
Secondly, three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of three cylindrical eccentric roundels 52 to move in up-and-down displacement.
Thirdly, when the conventional tubular eccentric roundel or cylindrical eccentric roundel 52 of the present invention moves in an up stroke with the piston acting zone 74 in up displacement, an acting force F will obliquely pull on the partial portion between the corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.
By comparing the operation of the conventional tubular eccentric roundels 52 shown in
In the case of conventional tubular eccentric roundel 52 shown in
Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area so that the magnitudes of the distributed components of the rebounding force Fs for the cylindrical eccentric roundels 52 of the present invention, as shown in
The improved distribution linearity and decreased magnitudes of the rebounding force components Fs result of forming the sloped top ring 58 between the annular positioning groove 55 and the vertical flank 56 in the eccentric roundel mount 50, and results in at least two advantages. First, this arrangement eliminates susceptibility to breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena, that occurs in the conventional arrangement as a result of the rounded shoulder 57 in the otherwise horizontal top face 53 of the tubular eccentric roundel 52. Second, the rebounding force Fs of the diaphragm membrane 70 caused by the acting force F, resulting from the sequential up-and-down displacement of the three piston acting zones 74 in the diaphragm membrane 70 driven by the up-and-down reciprocal stroke of the three tubular eccentric roundels or cylindrical eccentric roundels 52, is tremendously reduced.
These advantages result in the following practical benefits:
1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action of the cylindrical eccentric roundels 52 is substantially enhanced.
2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the squeezing phenomena at high frequencies.
3. The working temperature of the compressing diaphragm pump is tremendously reduced due to the decrease in power consumption.
4. The undesirable bearing noise caused by aging of the lubricant in the compressing diaphragm pump, which is normally accelerated by the high working temperature, is mostly eliminated.
Test results carried out on a prototype of the present invention are as follows.
A. The service lifespan of the tested diaphragm membrane 70 is was more than doubled.
B. The reduction in electric current consumption exceeded 1 ampere.
C. The working temperature was reduced by over 15 degrees Celsius.
D. The smoothness of the bearing was improved.
As shown in
As shown in
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
Referring to
Each pair of basic curved protrusions 77 and second outer curved protrusion 78 at the bottom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding basic curved grooves 65 and second outer curved grooves 66 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in the enlarged portion of
The shortened length of moment arm L2 not only has a significant effect in reducing vibration but also enhances stability by preventing displacement and maintaining the length of moment arm L2 to resist the acting force F on the eccentric roundel 52.
As shown in
As shown in
Each pair of basic curved protrusions 651 and second outer curved protrusions 661 at the upper side of the pump head body 60 is completely inserted into each corresponding pair of basic curved grooves 771 and second outer curved grooves 781 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Referring to
Each basic protruded ring 701 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding basic annular groove 601 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
As shown in
As shown in
Each basic protruding ring 610 at the upper side of the pump head body 60 is completely inserted into each corresponding basic annular groove 710 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Referring to
Each pair of curved protruding segments 702 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding pair of curved indented segments 602 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
As shown in
As shown in
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
Referring to
Each group of round protrusions 703 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of round openings or holes 603 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
As shown in
As shown in
Each group of round protrusions 630 at the upper side of the pump head body 60 is completely inserted into each group of corresponding round openings or holes 730 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Referring to
A group of square openings or holes 604 are further circumferentially disposed around each operating hole 61 in the pump head body 60 (as shown in
Each group of square protrusions 704 at the bottom side of the diaphragm membrane 70 is completely inserted into each corresponding group of square openings or holes 604 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
As shown in
As shown in
Each group of square protrusions 640 at the upper side of the pump head body 60 is completely inserted into each group of corresponding square openings or holes 740 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Referring to
Each pair of first inner protruding rings 705 and second outer protruding rings 706 at the bottom side of the diaphragm membrane 70 is completely inserted into each pair of corresponding first inner annular grooves 605 and second outer annular grooves 606 at the upper side of the pump head body 60 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
As shown in
As shown in
Each pair of first inner protruding rings 650 and second outer protruding rings 660 at the upper side of the pump head body 60 is completely inserted into each corresponding pair of first inner annular grooves 750 and second outer annular grooves 760 at the bottom side of the diaphragm membrane 70 upon assembly of the pump head body 60 and the diaphragm membrane 70 (as shown in
Please refer to
In this variation, the cylindrical eccentric roundel 52 is modified into an inverted frustoconical eccentric roundel 502 in an eccentric roundel mount 500.
The frustoconical eccentric roundel 502 includes an integral inverted frustoconical flank 506 and a sloped top ring 508 such that the outer diameter of the frustoconical eccentric roundel 502 is enlarged but still smaller than the inner diameter of the operating hole 61 in the pump head body 60, as well as the sloped top ring 508 extending between an annular positioning groove 505 and the inverted frustoconical flank 506.
Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that the three frustoconical eccentric roundels 502 on the eccentric roundel mount 500 constantly move in a sequential up-and-down reciprocal stroke.
Secondly, the three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three frustoconical eccentric roundels 502 to move in up-and-down displacement.
Thirdly, when the frustoconical eccentric roundel 502 in the present invention moves in an up stroke so that piston acting zone 74 is displaced upwardly, the acting force F will obliquely pull the partial portion between the corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.
Consequently, the inclusion of the sloped top ring 508 in the eccentric roundel mount 500 eliminates breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena that would otherwise result from the rounded shoulder 57 in the conventional tubular eccentric roundel 502 (as indicated in
Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area. By means of the enlarged outer diameter of the inverted frustoconical eccentric roundel 502, the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in
The inverted frustoconical eccentric roundel 502 of this embodiment of the present invention therefore provides at least some of the following benefits:
1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action is substantially increased as a result of the inverted frustoconical eccentric roundel 502.
2. The power consumption of the compressing diaphragm pump is tremendously diminished due to less current being wasted as a result of the high frequency squeezing phenomena.
3. The working temperature of the compressing diaphragm pump is tremendously reduced due to less power consumption.
4. The undesirable bearing noise resulting from aged lubricant in the compressing diaphragm pump, which is exacerbated by accelerated aging due to a high working temperature, is mostly eliminated.
5. The service lifespan of the compressing diaphragm pump is further prolonged because all distributed components of the rebounding force Fs for the inverted frustoconical eccentric roundels 502 of the present invention are reduced.
Firstly, the frustoconical roundel yoke 521 is fitted over the roundel mounts 511.
Secondly, all three annular positioning protrusions 76 of the diaphragm membrane 70 are inserted into three corresponding positioning annular grooves 515 in the three combinational eccentric roundels 502 of the eccentric roundel mount 500.
Finally, each fastening screw 1 is inserted through a corresponding tiered hole 81 of the pumping piston 80 and each corresponding acting zone hole 75 in the piston acting zones 74 of the diaphragm membrane 70, and then the fastening screw 1 is securely screwed into the three corresponding female-threaded bores 514 in the three roundel mounts 511 of the eccentric roundel mount 500 to firmly assembly the diaphragm membrane 70 and three pumping pistons 80 (as shown in
Firstly, when the motor 10 is powered on, the wobble plate 40 is driven to rotate by the motor output shaft 11 so that three combinational eccentric roundels 502 on the eccentric roundel mount 50 constantly move in a sequential up-and-down reciprocal stroke.
Secondly, the three piston acting zones 74 in the diaphragm membrane 70 are sequentially driven by the up-and-down reciprocal stroke of the three combinational eccentric roundels 502 to move in up-and-down displacement.
Thirdly, when the combinational eccentric roundel 502 in the present invention moves in an up stroke to displace the piston acting zone 74 upwardly, the acting force F will obliquely pull the partial portion between corresponding annular positioning protrusion 76 and outer raised rim 71 of the diaphragm membrane 70.
Consequently, the inclusion of the sloped top ring 526 in the inverted frustoconical roundel yoke 521 of the eccentric roundel mount 500 eliminates susceptibility to breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena that would otherwise result from the rounded shoulder 57 in the conventional tubular eccentric roundel indicated in
Moreover, under the same acting force F, the rebounding force Fs is inversely proportional to the contact area. By means of the enlarged outer diameter of the inverted frustoconical roundel yoke 521, the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in
The fabrication of this adaptation of the compressing diaphragm pump with multiple effects of the eighth exemplary embodiment of the present invention is as follows:
Firstly, the roundel mount 511 and eccentric roundel mount 500 are fabricated together as an integral body.
Secondly, the frustoconical roundel yoke 521 is independently fabricated as a separate entity.
Finally, the frustoconical roundel yoke 521 and the integral body of the roundel mount 511 are assembled with eccentric roundel mount 500 to become a united entity and form the assembled eccentric roundel 502 best shown in
Thereby, the contrivance of the combinational eccentric roundel 502 not only meets the requirement of mass production but also reduces the overall manufacturing cost.
The eccentric roundel 502 with frustoconical roundel yoke 521 of the present invention provides at least some of the following benefits:
1. The durability of the diaphragm membrane 70 for sustaining the high frequency pumping action is substantially increased by including the inverted frustoconical roundel yoke 521.
2. The power consumption of the compressing diaphragm pump is tremendously reduced due to less current being wasted as a result of the high frequency squeezing phenomena.
3. The working temperature of the compressing diaphragm pump is tremendously reduced due to the reduction in power consumption.
4. The undesired bearing noise resulting from temperature-accelerated aging of the lubricant in the compressing diaphragm pump is mostly eliminated.
5. The service lifespan of the compressing diaphragm pump is further prolonged because all distributed components of the rebounding force Fs for the inverted frustoconical roundel yoke 521 of the present invention are further reduced.
6. The manufacturing cost of the compressing diaphragm pump is reduced because the present invention is suitable for mass production.
As described above, the present invention substantially achieves a vibration reducing effect in the compressing diaphragm pump by means of a simple newly devised mating means for the pump head body and diaphragm membrane without increasing overall cost, so that it solves all issues of vibration-induced noise and resonant shaking that occurs in the conventional compressing diaphragm pump. Additionally, by means of simple sloped top ring for various cylindrical eccentric roundels of the present invention, the service lifespan of the diaphragm membrane in the compressing diaphragm pump can be doubled, which has valuable industrial applicability.
This application claims the benefit of provisional U.S. Patent Application No. 62/000,597, filed May 20, 2014, and incorporated herein by reference.
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