EP3146211A1 - Eccentric roundel structure for compressing diaphragm pump with multiple effects - Google Patents
Eccentric roundel structure for compressing diaphragm pump with multiple effectsInfo
- Publication number
- EP3146211A1 EP3146211A1 EP15796445.3A EP15796445A EP3146211A1 EP 3146211 A1 EP3146211 A1 EP 3146211A1 EP 15796445 A EP15796445 A EP 15796445A EP 3146211 A1 EP3146211 A1 EP 3146211A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- eccentric
- roundel
- mount
- piston
- eccentric roundel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/04—Pumps having electric drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0045—Special features with a number of independent working chambers which are actuated successively by one mechanism
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/0009—Special features
- F04B43/0054—Special features particularities of the flexible members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
Definitions
- the present invention relates to an eccentric roundel structure for a compressing diaphragm pump used in a reverse osmosis (RO) purification system, and particularly to a compressing diaphragm pump with a sloped top ring 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.
- RO reverse osmosis
- 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 arranged such that each end of the radial raised partition ribs 73 connects with the inner raised rim 72, thereby forming three equivalent piston acting zones 74 partitioned by the radial raised partition ribs 73.
- Each piston acting zone 74 has an acting zone hole 75 created therein in correspondence with a respective female-threaded bore 54 in the tubular eccentric roundel 52 of the eccentric roundel mount 50, and an annular positioning protrusion 76 for each acting zone hole 75 is formed at the bottom side of the diaphragm membrane 70 (as shown in FIGS. 8 and 9).
- Each pumping piston 80 is respectively disposed in a respective one of the corresponding piston acting zones 74 of the diaphragm membrane 70 and has a tiered hole 81 extending therethrough.
- Piston valvular assembly 90 covers the diaphragm membrane 70 and includes a downwardly extending raised rim 91 for insertion between the outer raised rim 71 and inner raised rim 72 in the diaphragm membrane 70, and 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.
- the piston valvular assembly 90 also includes 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.
- a hermetically sealed preliminary-compression chamber 26 is formed between each inlet mount 96 and a corresponding piston acting zone 74 in the diaphragm membrane 70 upon insertion of the downwardly extending raised rim 91 into the gap ring between the outer raised rim 71 and inner raised rim 72 of diaphragm membrane 70, such that one end of each preliminary-compressing chamber 26 is in communication with each of the corresponding inlet ports 97 (as shown in the enlarged portion of FIG. 10).
- the pump head cover 20 which covers the pump head body 60 to encompass the piston valvular assembly 90, pumping piston 80 and diaphragm membrane 70 therein, includes a water inlet orifice 21, a water outlet orifice 22, and several fastening bores 23.
- a tiered rim 24 and an annular rib ring 25 are disposed in the bottom inside of the pump head cover 20 such that the outer rim for the assembly of diaphragm membrane 70 and piston valvular assembly 90 can be hermetically attached to the tiered rim 24 (as shown in the enlarged portion of FIG. 11).
- a high-compression chamber 27 is formed between the cavity formed by the inside wall of the annular rib ring 25 and the central outlet mount 92 of the piston valvular assembly 90 when the bottom of the annular rib ring 25 closely covers the rim of the central outlet mount 92 (as shown in FIG. 10).
- FIGS. 11 and 12 are illustrative figures for the operation of the conventional compressing diaphragm pump of Figs. 1-10.
- 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.
- 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.
- the pressurized water Wp in the preliminary-compression chamber 26 is directed into high-compression chamber 27 via the group of outlet ports 95 for the corresponding sector in the central outlet mount 92, and then expelled out of the water outlet orifice 22 in the pump head cover 20 (as indicated by arrowhead W in the enlarged portion of FIG. 12).
- the squeezing phenomenon occurs because, among all of the distributed components of the rebounding force Fs, the maximum component force is exerted at the contacting bottom position P of the diaphragm membrane 70 with the rounded shoulder 57 of the horizontal top face 53 in the tubular eccentric roundel 52 so that the squeezing phenomenon at the bottom position P is also maximum, as shown in FIG. 18.
- 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.
- An objective of the present invention is to provide a compressing diaphragm pump, in which the eccentric roundel structure is a cylindrical or inverted frustoconical eccentric roundel disposed in an eccentric roundel mount, the cylindrical or inverted frustoconical eccentric roundel including an annular positioning groove, a vertical or frustoconical 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.
- the sloped top ring 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 to the bottom area of a corresponding piston acting zone of the diaphragm membrane.
- Yet another objective of the present invention is to provide an eccentric roundel for a compressing diaphragm pump, in which the eccentric roundel structure is a cylindrical or inverted frustoconical eccentric roundel disposed on an eccentric roundel mount, the eccentric roundel including an annular positioning groove, a vertical or frustoconical flank, and a sloped top ring formed between the annular positioning groove and the vertical or frustoconical flank.
- 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.
- FIG. 1 is a perspective assembled view of a conventional compressing diaphragm pump.
- FIG. 2 is a perspective exploded view of a conventional compressing diaphragm pump.
- FIG. 3 is a perspective view of an eccentric roundel mount for the conventional compressing diaphragm pump.
- FIG. 4 is a cross sectional view taken against the section line 4-4 from previous
- FIG. 5 is a top view of a pump head body for the conventional compressing diaphragm pump.
- FIG. 6 is a cross sectional view taken against the section line 6-6 from previous FIG. 5.
- FIG. 7 is a perspective view of a diaphragm membrane for the conventional compressing diaphragm pump.
- FIG. 8 is a cross sectional view taken against the section line 8-8 from previous
- FIG. 7 is a bottom view of a diaphragm membrane for the conventional compressing diaphragm pump.
- FIG. 10 is a cross sectional view taken against the section line 10-10 from previous FIG. 1.
- FIG. 11 is a first operation illustrative view of a conventional compressing diaphragm pump.
- FIG. 12 is a second operation illustrative view of a conventional compressing diaphragm pump.
- FIG. 13 is a third operation illustrative view of a conventional compressing diaphragm pump.
- FIG. 14 is a partially enlarged view taken from circled-portion-a of previous FIG.
- FIG. 15 is a perspective exploded view of a first exemplary embodiment of the present invention.
- FIG. 16 is a perspective view of an eccentric roundel mount in the first exemplary embodiment of the present invention.
- FIG. 17 is a cross sectional view taken against the section line 17-17 from previous FIG. 16.
- FIG. 18 is an assembled cross sectional view of the first exemplary embodiment of the present invention.
- FIG. 19 is an operation illustrative view of the first exemplary embodiment of the present invention.
- FIG. 20 is a partially enlarged view taken from circled-portion-a of previous FIG.
- FIG. 21 is an illustrative view showing a comparison between the eccentric cylindrical roundel acting on the diaphragm membrane of the conventional compressing diaphragm pump and that of the first exemplary embodiment of the present invention.
- FIG. 22 is a perspective view for eccentric roundel mount in the second exemplary embodiment of the present invention.
- FIG. 23 is a cross sectional view taken against the section line 23-23 from previous FIG. 22.
- FIG. 24 is an assembled cross sectional view for the second exemplary embodiment of the present invention.
- FIG. 25 is an operation illustrative view of the second exemplary embodiment of the present invention.
- FIG. 26 is a partially enlarged view taken from circled-portion-a of previous FIG. 25.
- FIG. 27 is an illustrative view showing a comparison between the eccentric cylindrical roundel acting on the diaphragm membrane for the conventional compressing diaphragm pump and for the present invention in the second exemplary embodiment of the present invention.
- FIG. 28 is a perspective exploded view for the third exemplary embodiment of the present invention.
- FIG. 29 is a cross sectional view taken against the section line 29-29 from previous FIG. 28.
- FIG. 30 is a perspective assembled view for the third exemplary embodiment of the present invention.
- FIG. 31 is a cross sectional view taken against the section line 31-31 from previous FIG. 30.
- FIG. 32 is an assembled cross sectional view for the third exemplary embodiment of the present invention.
- FIG. 33 is an operation illustrative view for the third exemplary embodiment of the present invention.
- FIG. 34 is a partially enlarged view taken from circled-portion-a of previous FIG.
- FIG. 35 is an illustrative view showing a comparison between the eccentric cylindrical roundel acting on the diaphragm membrane for the conventional compressing diaphragm pump and for the present invention in the third exemplary embodiment of the present invention.
- FIGS. 15 through 18 are illustrative figures of an eccentric roundel structure for compressing diaphragm pump according to a first exemplary embodiment of the present invention.
- the eccentric roundel structure is a cylindrical eccentric roundel 52 that is mounted on the eccentric roundel mount 50.
- the cylindrical eccentric roundel 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.
- FIGS. 19 through 21 are illustrative figures for the operation of the eccentric roundel structure for compressing diaphragm pump" in the first exemplary embodiment of the present invention.
- 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.
- the 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.
- the distribution of components of the rebounding force Fs is more linear because the sloped top ring 58 therein flatly attaches to the bottom area of the piston acting zone 74 for the diaphragm membrane 70, so that the oblique pulling action is almost eliminated due to reduction in the squeezing phenomenonl920.
- the rebounding force Fs is inversely proportional to the contact area so that the magnitudes of the distributed components of the rebounding force Fs for the cylindrical eccentric roundels 52 of the present invention, as shown in FIG. 20, are substantially less than the magnitudes of the distributed components of the rebounding force Fs for the conventional tubular eccentric roundel 52 shown in FIG. 14.
- the improved distribution linearity and decreased magnitudes of the rebounding force components Fs are the 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 in turn provides at least the following advantages.
- the improved force component distribution eliminates susceptibility to breakage of the diaphragm membrane 70 caused by the high frequency squeezing phenomena, that occurs in the conventional arrangement as a result of the rounded shoulder 57 in the otherwise horizontal top face 53 of the tubular eccentric roundel52.
- Test results carried out on a prototype of the present invention are as follows. A. The service lifespan of the tested diaphragm membrane 70 was more than doubled.
- FIGS. 22 through 24 are illustrative figures of an eccentric roundel structure for compressing diaphragm pump in the second exemplary embodiment of the present invention
- the eccentric roundel structure is an inverted frustoconical eccentric roundel 502, again provided on 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, the sloped top ring 508 extending between an annular positioning groove 505 and the inverted frustoconical flank 506.
- FIGS. 25 through 27 are illustrative figures showing the modified operation of the eccentric roundel structure for compressing diaphragm pump in the second exemplary embodiment of the present invention.
- 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.
- 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.
- the rebounding force Fs is inversely proportional to the contact area.
- the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in FIG. 27) so that all distributed components of the rebounding force Fs for the inverted frustoconical eccentric roundels 502 of the present invention are further reduced.
- the inverted frustoconical eccentric roundel 502 of this embodiment of the present invention therefore provides at least some of the following benefits:
- 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.
- the working temperature of the compressing diaphragm pump is tremendously reduced due to less power consumption.
- the service lifespan of the compressing diaphragm pump is further prolonged because all distributed components of the rebounding force Fs for the inverted frustoconical eccentric roundels 502 of the present invention are reduced.
- FIGS. 28 through 31 are illustrative figures of eccentric roundel structure for compressing diaphragm pump in the third exemplary embodiment of the present invention, in which the eccentric roundel structure is a combinational eccentric roundel 502 in an eccentric roundel mount 500.
- the combinational eccentric roundel 502 includes a roundel mount 511 and an inverted frustoconical roundel yoke 521 in detachable separation such that the outer diameter of the frustoconical roundel yoke 521 is enlarged but still smaller than the inner diameter of the operating hole 61 in the pump head body 60.
- the roundel mount 511 has two layers that include a bottom-layer base with a positioning crescent surface 512 facing inwardly and a top-layer protruding cylinder 513 with a central female-threaded bore 514.
- the inverted frustoconical roundel yoke 521 is sleeved over the corresponding roundel mount 511 and includes an upper bore 523, a middle bore 524 and a lower bore 525 stacked as a three-layered integral hollow structure, as well as an inverted frustoconical flank 522 and a sloped top ring 526 extending from the upper bore 523 to the inverted frustoconical flank 522 such that the bore diameter of the upper bore 523 is bigger than the outer diameter of the protruding cylinder 513.
- the bore diameter of the middle bore 524 is approximately equal to the outer diameter of the protruding cylinder 513, such that the bore diameter of the lower bore 525 is approximately equal to the outer diameter of the bottom-layer
- a positioning annular groove 515 is formed between the protruding cylinder 513 and the inside wall of the upper bore 523 when the frustoconical roundel yoke 521 is sleeved over the roundel mounts 511 (as shown in FIGS. 30 and 31).
- FIGS. 32 and 35 illustrate the manner in which the eccentric roundel structure for compressing diaphragm pump third exemplary embodiment of the present invention is assembled.
- each fastening screw 1 is inserted through a corresponding tiered hole 81 of the pumping piston 80 and each corresponding acting zone hole 75 in the piston acting zones 74 of the diaphragm membrane 70, and then the fastening screw 1 is securely screwed into the three corresponding female-threaded bores 514 in the three roundel mounts 511 of the eccentric roundel mount 500 to firmly assembly the diaphragm membrane 70 and three pumping pistons 80 (as shown in FIG. 32).
- FIGS. 33 and 34 illustrate the operation of the eccentric roundel structure for compressing diaphragm pump of the third exemplary embodiment of the present invention.
- 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.
- 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.
- 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 the corresponding annular positioning protrusion 76 and the 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 (as shown in FIGS. 33 and 34) and also causes the rebounding force Fs of the diaphragm membrane 70 caused by the acting force F to be tremendously reduced (as shown in FIG. 34).
- the rebounding force Fs is inversely proportional to the contact area.
- the contact area of the sloped top ring 508 with the bottom side of the diaphragm membrane 70 is increased (as indicated by ring A shown in FIG. 35) so that all distributed components of the rebounding force Fs for the inverted frustocomcal roundel yoke 521 of the present invention are further reduced.
- roundel mount 511 and eccentric roundel mount 500 are fabricated together as an integral body.
- the frustocomcal roundel yoke 521 is independently fabricated as a separate entity. Finally, the frustocomcal roundel yoke 521 and the integral body of the roundel mount 511 are assembled with eccentric roundel mount 500 to become a united entity and form the assembled eccentric roundel 502 best shown in FIGS. 108 and 109.
- the eccentric roundel 502 with frustocomcal roundel yoke 521 of the present invention provides at least some of the following benefits:
- the durability of the diaphragm membrane 70 for sustaining the high frequency pumping action is substantially increased by including the inverted frustocomcal roundel yoke 521.
- 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.
- the working temperature of the compressing diaphragm pump is tremendously reduced due to the reduction in power consumption.
- 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.
- the manufacturing cost of the compressing diaphragm pump is reduced because the present invention is suitable for mass production.
- the illustrated embodiments of the invention provide a cylindrical eccentric roundel 52, an inverted frustoconical eccentric roundel 502, or combinational eccentric roundel 502 that, among other advantages, increases the service lifespan of the diaphragm membrane 70 so that the service lifespan of the compressing diaphragm pump can be doubled.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201462000630P | 2014-05-20 | 2014-05-20 | |
PCT/US2015/028137 WO2015179087A1 (en) | 2014-05-20 | 2015-04-29 | Eccentric roundel structure for compressing diaphragm pump with multiple effects |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3146211A1 true EP3146211A1 (en) | 2017-03-29 |
EP3146211A4 EP3146211A4 (en) | 2018-02-14 |
Family
ID=54554521
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15796445.3A Withdrawn EP3146211A4 (en) | 2014-05-20 | 2015-04-29 | Eccentric roundel structure for compressing diaphragm pump with multiple effects |
Country Status (3)
Country | Link |
---|---|
US (1) | US20150337816A1 (en) |
EP (1) | EP3146211A4 (en) |
WO (1) | WO2015179087A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3327287B1 (en) * | 2016-11-23 | 2024-05-15 | PSG Germany GmbH | Membrane pump |
US10859080B2 (en) * | 2017-11-03 | 2020-12-08 | Xiamen Koge Micro Tech Co., Ltd. | Valve head structure for diaphragm pump and diaphragm pump having same |
CN112128089B (en) * | 2020-09-27 | 2021-09-21 | 深圳华星恒泰泵阀有限公司 | Precision controllable metering diaphragm water pump |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2748606A (en) * | 1951-11-30 | 1956-06-05 | Cornelius Co | Mechanical movement |
DE3233853A1 (en) * | 1982-09-11 | 1984-03-15 | Erich 7812 Bad Krozingen Becker | PUMP WITH PISTON AND SLIDING SEAL |
US4915018A (en) * | 1988-09-13 | 1990-04-10 | American Standard Inc. | Diaphragm piston assembly |
DE3838141C2 (en) * | 1988-11-10 | 1998-12-24 | Knf Neuberger Gmbh | Diaphragm pump |
DE3943585C2 (en) * | 1989-08-31 | 1995-04-27 | Wagner Gmbh J | Diaphragm pump |
FR2689014B1 (en) * | 1992-03-24 | 1994-06-03 | Aguettant Lab | MEDICAL LIQUID PERFUSION PUMP. |
DE4328559C5 (en) * | 1993-08-25 | 2004-11-25 | Knf-Neuberger Gmbh | Diaphragm pump with at least two membranes |
US5476367A (en) * | 1994-07-07 | 1995-12-19 | Shurflo Pump Manufacturing Co. | Booster pump with sealing gasket including inlet and outlet check valves |
US6276907B1 (en) * | 1999-08-12 | 2001-08-21 | Wagner Spray Tech Corporation | Hydraulically driven diaphragm pump |
JP4114639B2 (en) * | 2004-06-01 | 2008-07-09 | 株式会社豊田自動織機 | Diaphragm type pump |
DE102005039237A1 (en) * | 2005-08-19 | 2007-02-22 | Prominent Dosiertechnik Gmbh | motor-driven metering |
US7887304B2 (en) * | 2005-11-08 | 2011-02-15 | Ying Lin Cai | Method and structure of preventing water from leakage for the pressurized pump of diaphragm type |
DE102008035592B4 (en) * | 2008-07-31 | 2014-10-30 | Almatec Maschinenbau Gmbh | diaphragm pump |
US20100068082A1 (en) * | 2008-09-17 | 2010-03-18 | Ying Lin Cai | Leakage-Proof Contrivance for Upper Hood of Diaphragm Pump |
-
2015
- 2015-04-29 WO PCT/US2015/028137 patent/WO2015179087A1/en active Application Filing
- 2015-04-29 US US14/699,373 patent/US20150337816A1/en not_active Abandoned
- 2015-04-29 EP EP15796445.3A patent/EP3146211A4/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
WO2015179087A1 (en) | 2015-11-26 |
US20150337816A1 (en) | 2015-11-26 |
EP3146211A4 (en) | 2018-02-14 |
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