TWI588358B - Roundel structure for four-compression-chamber diaphragm pump with multiple effects - Google Patents

Description

Improvement of the balance structure of the four-pressure diaphragm pump

The invention relates to a four-charged-cavity diaphragm pump installed in a reverse osmosis purification or a bathing water supply device in a recreational vehicle, in particular, a method capable of eliminating the four-pressure chamber When the diaphragm pump is actuated, the rounded top surface of the cylindrical balance wheel improves the balance of the diaphragm on the bottom surface of the diaphragm, and greatly improves the tolerance and extension of the diaphragm to withstand the high frequency pushing effect of the cylindrical balance. The life of the entire four plenum diaphragm pump.

The four-charged-cavity diaphragm pump currently used in the reverse osmosis water filter and the bath and kitchen water supply equipment in the travel car, in addition to being disclosed, for example, in U.S. Patent No. 6,840,745, is similar to the U.S. Patent No. 6,840,745 and is similar to A conventionally used four-please diaphragm pump structure, as shown in FIGS. 1 to 10, is composed of a motor 10, a motor front cover 30, a tilting eccentric cam 40, a balance wheel seat 50, and a pump head. The seat 60, a diaphragm piece 70, a four-piston push block 80, a piston valve body 90 and a pump head cover 20 are combined; wherein a bearing 31 is embedded in the center of the motor front cover 30, and is passed through the output shaft 11 of the motor 10. a ring-shaped upper convex ring 32 is protruded upwardly from the outer periphery thereof, and a plurality of fixed through holes 33 are formed on the inner edge surface and the outer edge surface of the upper convex ring 32; a shaft hole 41 is inserted through the center of the inclined eccentric cam 40; The sleeve 10 can be sleeved on the output shaft 11 of the motor 10; the center of the base of the balance seat 50 is embedded with a balance bearing 51, which can be placed on the inclined eccentric cam 40, and the top surface of the seat is equidistant Four cylindrical balance wheels 52 are arranged at intervals, and the horizontal top surface 53 of each cylindrical balance wheel 52 is concavely disposed. Screw a hole 54 and a recessed positioning groove 55 at the periphery of the threaded hole 54, and a horizontal top surface 53 and a vertical side surface 56 intersecting with a rounded corner 57; the pump head The seat 60 is sleeved on the upper convex ring 32 of the motor front cover 30, and the top surface thereof is provided with four actuating holes 61 which are equally spaced and larger than the outer diameters of the four cylindrical balance wheels 52 of the balance wheel seat 50, so that The four cylindrical balance wheels 52 can be placed in the four actuating perforations 61, and the bottom surface thereof is provided with a downward convex ring 62. The dimensions of the lower convex ring 62 and the upper convex ring 32 of the motor front cover 30. The same scale, the top surface of the outer peripheral edge is directed downwardly from the convex ring 62, and a plurality of fixed perforations 63 are formed. The diaphragm piece 70 is placed on the top surface of the pump head block 60 and is formed by semi-rigid elastic material. The outermost peripheral edge of the outer circumference is provided with two annularly opposite outer convex strips 71 and inner convex strips 72, and four ribs connected to the inner convex strip 72 are radiated from the central position of the top surface. 73. Between the four ribs 73 and the inner rib 72, four piston actuating regions 74 are spaced apart, and each piston actuating region 74 corresponds to each cylindrical pendulum in the balance ring 50. 52 positions of the threaded holes 54 of the top surface are respectively provided with a central through hole 75, and a positioning convex ring block 76 is protruded from the bottom surface of the diaphragm piece 70 located at each central through hole 75 (as shown in FIGS. 8 and 9). The four-piston push block 80 is respectively disposed in the four piston actuating regions 74 of the diaphragm piece 70. Each of the piston push blocks 80 is provided with a stepped hole 81, and four positioning convex rings on the bottom surface of the diaphragm piece 70 are disposed. The blocks 76 are respectively inserted into the positioning ring grooves 55 of the four cylindrical balance wheels 52 of the balance wheel seat 50, and then inserted into the stepped holes 81 of the piston push block 80 by the fixing screws 1 and passed through the diaphragm piece 70. After the central perforation 75 of the four piston actuating regions 74, the diaphragm piece 70 and the four-piston push block 80 can be screwed into the threaded holes 54 of the four cylindrical balance wheels 52 of the balance wheel housing 50 (as shown in the enlarged view in FIG. 10). An annular ring ridge 91 is protruded downwardly from the outer peripheral side surface of the bottom of the piston valve body 90, and is inserted into a gap between the outer rib 71 and the inner rib 72 of the diaphragm 70, which faces the pump head cover 20. A circular drain seat 92 having a concave curved surface is disposed at a central position of the direction, and a positioning hole 93 is formed in the center of the drain seat 92 for a T type Penetrate the check pad 94 is fixed to the other fixed The positional holes 93 are formed at four regional positions separated by an angle of 90 degrees, each of which is provided with a plurality of drainage holes 95, and the peripheral faces of the drainage seats 92 corresponding to the four regional drainage holes 95 are respectively connected to each other. Four inlet seats 96 are arranged at an angle of 90 degrees and each of the openings are downwardly facing. A plurality of inlet holes 97 are formed in each of the inlet seats 96, and a handstand is placed in the center of each inlet seat 96. The T-shaped piston piece 98 can block the water inlet holes 97 by the piston piece 98. The drainage holes 95 in the four areas of the drainage seat 92 are respectively connected to the corresponding four water inlets 96. After the ring rib 91 at the bottom of the piston valve body 90 is inserted into the gap between the outer rib 71 of the diaphragm 70 and the inner rib 72, the top surface of each of the water inlet 96 and the diaphragm 70 can be provided. Between the two, a closed plenum chamber 26 is formed (as shown in FIG. 10 and its enlarged view); the pump head cover 20 is disposed on the pump head housing 60, and a water inlet 21 and a rim are provided on the outer edge surface thereof. The water outlet 22 and the plurality of fixed perforations 23, and the bottom ring of the inner edge surface is provided with a stepped groove 24, so that the diaphragm piece 70 and the piston valve body 90 are superposed on each other The outer edge can be closely attached to the stepped groove 24 (as shown in the enlarged view in FIG. 10), and a ring of convex rings 25 is arranged in the center of the inner edge surface, and the bottom of the convex ring 25 is compressed. In the outer peripheral surface of the drain seat 92 of the piston valve body 90, a space between the inner wall surface of the convex ring 25 and the drain seat 92 of the piston valve body 90 can be formed around the high pressure water chamber 27 (as shown in FIG. 10). ), through the fixing bolts 2 respectively passing through the respective fixing through holes 23 of the pump head cover 20, and through the fixing perforations 63 of the pump head holder 60, and then the nuts inserted into the fixing holes 33 in the motor front cover 30 The three-phase screwing can complete the combination of the entire four-pressure chamber diaphragm pump (as shown in Figures 1 and 10).

As shown in FIG. 11 and FIG. 12, it is the operation mode of the above-mentioned conventional four-pressure chamber diaphragm pump. When the output shaft 11 of the motor 10 rotates, the tilting eccentric cam 40 is rotated, and at the same time, the balance wheel housing 50 is The four cylindrical balance wheels 52 sequentially generate up and down reciprocating motions, and the four piston actuating regions 74 on the diaphragm piece 70 are also actuated by the four cylindrical balance wheels 52, which are sequentially synchronized. Pushing up and down to produce a reverse up and down displacement, so when the cylindrical balance 52 is actuated downward, the piston actuation zone 74 and the piston pusher block 80 of the diaphragm 70 are simultaneously pulled down, so that the piston valve body 90 The piston piece 98 is pushed open, and the tap water W from the water inlet hole 21 of the pump head cover 20 is introduced into the plenum chamber 26 via the water inlet hole 97 (as indicated by an arrow W in FIG. 11 and its enlarged view); When the cylindrical balance wheel 52 pushes up, the piston actuating zone 74 and the piston pusher block 80 of the diaphragm 70 are simultaneously topped up, and the water in the pressurizing chamber 26 is squeezed to make water pressure. Increasing to between 100 psi and 150 psi, the pressurized high pressure water Wp can push the check rubber pad 94 on the drain seat 92 away, and continuously flow into the high pressure water chamber through the drain holes 95 of the drain seat 92. 27, and then discharged through the water outlet 22 of the pump head cover 20 outside the four plenum diaphragm pump (as shown by arrow Wp in FIG. 12 and its enlarged view), thereby providing an inverse of the RO membrane tube in the reverse osmosis water filter. The water pressure required for osmotic filtration, or the water pressure required for the output of the bath and water supply equipment in the RV.

As shown in FIG. 13 and FIG. 14 , when the above-mentioned four plenum diaphragm pump is actuated, the four cylindrical balance wheels 52 are pushed by the rotation of the tilting eccentric cam 40, and each of the diaphragm plates 70 is pushed upwards. A piston actuating zone 74, which is equal to the position of the four piston actuating zones 74 on the bottom surface of the diaphragm 70, is continuously applied with an upward force F, and each time the bottom surface of the diaphragm 70 is pushed up by the force F, The downward bucking force Fs is also generated synchronously, and the magnitude distribution of the force acts on the diaphragm piece 70 on each piston actuating zone 74 (as indicated by the distribution arrow of each size rebounding force Fs in Fig. 14). The bottom surface of the diaphragm 70 at the position of the four piston actuation zones 74 is caused to be squeezed, wherein the diaphragm 70, which is in contact with the intersection of the horizontal top surface 53 and the rounded corner 57 in the cylindrical balance 52, is again provided. The bottom surface position P is subjected to the greatest degree of squeezing (as shown in FIG. 14). Therefore, at the rotational speed of the output shaft 11 of the motor 10 up to 800-1200 rpm, the bottom surface position P of each piston actuation region 74 in the diaphragm 70 is At least 4 times per second squeezed, but at such a high frequency At the rate of extrusion, the bottom surface position P of the diaphragm 70 is the earliest position where the crack is generated, and the main reason why the entire four-pressure diaphragm pump can no longer operate normally and reduce its service life is eliminated. The bottom surface of the diaphragm actuation region 74 of the diaphragm 70 is easily broken due to the high frequency pushing and pressing of the cylindrical balance 52, which is an urgent problem to be solved.

The main object of the present invention is to provide an "improvement of the balance structure of a four-charged diaphragm pump", which is to position the annular groove on the horizontal top surface of each cylindrical balance in the balance seat to the vertical side surface. The area is set to a downward slope so that after the motor output shaft of the four-pressure diaphragm pump rotates, the four cylindrical balance wheels are subjected to the tilting eccentric cam rotation to push up the bottom surface of the diaphragm of the piston actuation region, and the upward action The force causes the diaphragm body between the positioning cam ring and the outer rib in the diaphragm to be in an upwardly inclined state, and the annular groove is positioned on the horizontal top surface of each cylindrical balance to the vertical side surface. The downward inclined surface can be completely flatly supported on the bottom surface of the diaphragm actuating area of the diaphragm in the diagonally pulled state, and the squeezing and squeezing of the bottom surface of the diaphragm piston working area can be completely eliminated, so that the conventional four-increase can be completely eliminated. The rounding of the cylindrical balance wheel in the diaphragm pump of the pressure chamber is easy to break the high frequency extrusion of the bottom surface of the diaphragm piston working area, which can greatly improve the tolerance of the diaphragm piece to the high frequency pushing effect of the cylindrical balance wheel. And effective delay The life of the entire fourth plenum of the diaphragm pump.

Another object of the present invention is to provide an "improvement of the balance structure of a four-charged diaphragm pump", which is to position a circular groove to a vertical side surface on a horizontal top surface of each cylindrical balance in the balance seat. The area is set to a downward slope so that after the motor output shaft of the four-pressure diaphragm pump rotates, the four cylindrical balance wheels are rotated by the inclined eccentric cam to push up the bottom surface of the diaphragm of the piston actuation region, and the upward direction is The force will cause the diaphragm to be positioned between the convex ring and the outer rib Producing an upwardly inclined state, by positioning the annular groove on the horizontal top surface of each cylindrical balance to the downward slope of the vertical side surface, the surface of the diaphragm can be completely flatly supported at the same time. Without causing the squeezing and squeezing of the diaphragm surface of the diaphragm piston, the rebound force of the diaphragm is greatly reduced after the diaphragm is subjected to the upward force, so that the working current load and the operating temperature of the motor can be effectively reduced. In addition, the lubricating oil in the motor bearing does not cause high temperature evaporation, which leads to the lack of lubrication, resulting in the lack of abnormal sound, in addition to ensuring that all the bearings in the diaphragm booster pump are running smoothly, and the motor operating current is reduced. The expenditure on electricity and electricity costs also has multiple benefits such as extending the service life of the entire diaphragm booster pump.

1‧‧‧ fixing screws

2‧‧‧ fixing bolts

3‧‧‧ nuts

10‧‧‧ motor

11‧‧‧Output shaft

20‧‧‧ pump head cover

21‧‧‧ Inlet

22‧‧‧Water outlet

23, 33, 63 ‧ ‧ fixed perforation

24‧‧‧ stepped trough

25‧‧‧ convex ring

26‧‧‧Booster chamber

27‧‧‧High pressure water room

30‧‧‧Motor front cover

31‧‧‧ bearing

32‧‧‧Upper convex ring

40‧‧‧Slanted eccentric cam

41‧‧‧Axis hole

50,500‧‧‧wheel seat

51‧‧‧balance bearing

52, 502‧‧ ‧ cylindrical balance wheel

53, 503‧‧‧ horizontal top

54,514‧‧‧Threaded holes

55, 505, 515‧‧‧ positioning ring groove

56‧‧‧Vertical side faces

57‧‧‧round

58,508, 526‧‧‧ downward slope

60‧‧‧ pump head

61‧‧‧Actuation perforation

62‧‧‧Under convex ring

70‧‧‧ Diaphragm

71‧‧‧Outer ribs

72‧‧‧ inside ribs

73‧‧‧ ribs

74‧‧‧Piston action zone

75‧‧‧Central perforation

76‧‧‧ positioning convex ring block

80‧‧‧Piston push block

81‧‧‧step hole

90‧‧‧ piston valve body

91‧‧‧ ring ribs

92‧‧‧Drainage seat

93‧‧‧Positioning holes

94‧‧‧Reverse rubber pad

95‧‧‧Drainage holes

96‧‧‧Water inlet

97‧‧‧ water inlet hole

98‧‧‧Pneumatic blades

506, 522‧‧‧Inwardly inclined side faces

511‧‧‧Cylinder seat

512‧‧‧ positioning plane

513‧‧‧ convex cylinder

521‧‧‧balance ring

523‧‧‧Upper hole

524‧‧‧Medium hole

525‧‧‧lower hole

F‧‧‧force

Fs‧‧‧Rebound force

P‧‧‧ bottom position

W‧‧‧ tap water

Wp‧‧‧High pressure water

Figure 1: is a three-dimensional combination of the conventional four-pressure diaphragm pump.

Figure 2: An exploded perspective view of a conventional four-pressure chamber diaphragm pump.

Figure 3: is a perspective view of a cylindrical balance wheel in a conventional four-pressure diaphragm pump.

Figure 4 is a cross-sectional view taken along line 4-4 of Figure 3.

Figure 5: is a perspective view of a pump head seat in a conventional four-bore diaphragm pump.

Figure 6 is a cross-sectional view taken along line 6-6 of Figure 5. .

Figure 7 is a perspective view of a diaphragm in a conventional four-bore diaphragm pump.

Figure 8: Sectional view of line 8-8 in Figure 7

Figure 9 is a bottom view of a diaphragm in a conventional four-bore diaphragm pump.

Figure 10 is a cross-sectional view taken along line 10-10 of Figure 1.

Figure 11: One of the schematic diagrams of the operation of the conventional four-pressure diaphragm pump.

Figure 12: The second schematic diagram of the operation of the conventional four-pressure diaphragm pump.

Figure 13: The third schematic diagram of the operation of the conventional four-pressure diaphragm pump.

Figure 14 is an enlarged view of view a in Figure 13.

Figure 15 is an exploded perspective view showing a first embodiment of the present invention installed in a conventional four-pressure chamber diaphragm pump.

Figure 16 is a perspective view showing a first embodiment of the present invention.

Figure 17 is a cross-sectional view taken along line 17-17 of Figure 16.

Figure 18 is a cross-sectional view showing a first embodiment of the present invention installed in a conventional four-pressure chamber diaphragm pump.

Figure 19 is a schematic view showing the operation of the first embodiment of the present invention.

Figure 20: is an enlarged view of view a in Figure 19.

Figure 21 is a cross-sectional view showing a comparison of the first embodiment of the present invention and the cylindrical balance wheel of the conventional four-pressure chamber diaphragm pump, respectively, after pushing the diaphragm.

Figure 22 is a perspective view showing a second embodiment of the present invention.

Figure 23 is a cross-sectional view taken along line 23-23 of Figure 22.

Figure 24 is a cross-sectional view showing a second embodiment of the present invention installed in a conventional four-pressure chamber diaphragm pump.

Figure 25 is a schematic view showing the operation of the second embodiment of the present invention.

Figure 26: is an enlarged view of view a in Figure 25.

Figure 27 is a cross-sectional view showing a comparison between the second embodiment of the present invention and the conventional four-pilot diaphragm pump in which the cylindrical balance wheel is actuated to push the diaphragm.

Figure 28 is an exploded perspective view showing another embodiment of the cylindrical balance in the second embodiment of the present invention.

Figure 29 is a cross-sectional view taken along line 29-29 of Figure 28.

Figure 30 is a perspective assembled view of another embodiment of a cylindrical balance in a second embodiment of the present invention.

Figure 31 is a cross-sectional view taken along line 31-31 of Figure 30.

Figure 32 is a cross-sectional view showing another embodiment of the cylindrical balance wheel of the second embodiment of the present invention installed in a conventional four-pressure chamber diaphragm pump.

Figure 33 is a schematic view showing the operation of another embodiment of the cylindrical balance wheel according to the second embodiment of the present invention mounted on a conventional four-pressure chamber diaphragm pump.

Figure 34: is an enlarged view of view a in Figure 33.

Figure 35 is a cross-sectional view showing a comparison of another embodiment of the cylindrical balance wheel in the second embodiment of the present invention and the cylindrical balance wheel of the conventional four-pressure chamber diaphragm pump respectively actuating the diaphragm.

As shown in FIG. 15 to FIG. 18, in the first embodiment of the present invention, "the structure of the balance of the four plenum diaphragm pump is improved", the horizontal top surface 53 of each cylindrical balance 52 of the balance wheel housing 50 is shown. The upper positioning ring groove 55 to the vertical side surface 56 is provided with a downward slope 58.

As shown in FIG. 19 to FIG. 21, in the first embodiment of the present invention, "the structure of the balance of the four plenum diaphragm pump is improved", the four cylindrical balance wheels 52 are rotated by the tilting eccentric cam 40 to push up the piston. After the bottom surface of the diaphragm 70 of the actuating portion 74, the upward force F causes the diaphragm body between the positioning ring block 76 and the outer rib 71 in the diaphragm 70 to be inclined upwardly by the cylinder. A downward inclined surface 58 for positioning the annular groove 55 to the vertical side surface 56 on the horizontal top surface 53 of the balance wheel 52 can be completely flush contact and supported on the bottom surface of the piston actuation region 74 of the diaphragm sheet 70 in the diagonally pulled state. There is no phenomenon that the bottom surface of the diaphragm 70 actuation region 74 is crushed (as shown in FIGS. 19 and 20), and the rebound force Fs generated by the diaphragm 70 is also greatly reduced ( As shown by the arrow distribution of each size rebounding force Fs in FIG. 20, it is understood that the rebounding force Fs generated by the diaphragm 70 is greatly reduced by comparing the magnitude rebound force Fs of FIG. Therefore, by positioning the circle on the horizontal top surface 53 of the cylindrical balance 52 of the present invention The downward slope 58 of the groove 55 to the vertical side surface 56 can completely eliminate the rounded corner 57 of the cylindrical balance 52 in the conventional four-pressure diaphragm pump, and the bottom surface of the diaphragm 70 is activated by a high frequency 〝 The squeezing flaw causes the rupture of the rupture (as shown by the imaginary line portion in Fig. 21), and has the effect of greatly reducing the rebound force Fs when the diaphragm 70 is subjected to the upward force F, so that the diaphragm 70 can greatly improve the tolerance of the high-frequency pushing action of the cylindrical balance wheel 52, and can effectively reduce the working current load and working temperature of the motor, and thus the lubricating oil in the motor bearing will not cause high-temperature evaporation to cause lubrication. The lack of good noise, in addition to ensuring that all the bearings in the diaphragm booster pump are running smoothly, and reducing the power and electricity expenses due to the reduced operating current of the motor, and at the same time extending the service life of the entire diaphragm booster pump. Benefits, the invention is installed in a conventional four-pressure chamber diaphragm pump and the measured results show that the operating temperature of the motor 10 can be reduced by at least 15 ° C, the operating current can be reduced by more than 1 amp, and the diaphragm 70 and the entire four increase The service life of the diaphragm pump can be increased by more than two times.

As shown in FIG. 22 to FIG. 24, in the second embodiment of the present invention, "the structure of the balance of the four-pilot diaphragm pump is improved", the diameter of each cylindrical balance 502 in the balance wheel holder 500 is increased. However, it is still smaller than the inner diameter of the actuating perforation 61 in the pump head 60, and the side surface thereof is provided with an inwardly inclined side surface 506, and the annular groove is positioned on the horizontal top surface 503 of each cylindrical balance 502. The region 505 to the inwardly inclined side surface 506 is provided with a downward slope 508.

As shown in FIG. 25 to FIG. 27, when the second embodiment of the "four-pilot diaphragm pump improvement of the balance structure of the present invention" is actuated, the four cylindrical balance wheels 502 are rotated by the tilting eccentric cam 40 to push up the piston. When the bottom surface of the diaphragm 70 of the actuating portion 74 is actuated, the upward force F causes the diaphragm body between the positioning ring block 76 and the outer rib 71 in the diaphragm 70 to be inclined upwardly by the cylinder. A circular groove 505 is disposed on the horizontal top surface 503 of the balance wheel 502 to the downward slope 508 of the inwardly inclined side surface 506, and can be completely flush contact and supported on the bottom surface of the diaphragm sheet 70 in the diagonally inclined state, and The phenomenon that the bottom surface of the diaphragm 70 actuation region 74 is not crushed (as shown in FIGS. 25 and 26) is not generated, and the rebound force Fs generated by the diaphragm 70 is also greatly reduced (as shown in the figure). The arrow distribution of each size rebound force Fs is shown in 26), and the side surface 506 is inclined inward. The meter structure can be prevented from hitting the hole wall surface of the pump head 60 to actuate the through hole 61 when the diameter of the cylindrical balance wheel 502 is increased, so that the cylindrical balance wheel 502 of the present invention is used. The annular groove 505 is positioned on the horizontal top surface 503 to the downward slope 508 of the inwardly inclined side surface 506, except that the rounded corner 57 of the cylindrical balance 502 in the conventional four-pressure diaphragm pump can be completely eliminated. The bottom surface of the 70-piston actuation zone 74 is devoid of the defect of the squeezing squeezing (as shown by the imaginary line portion in Fig. 27), and has the effect of substantially reducing the rebound force Fs when the diaphragm 70 is subjected to the upward force F. Therefore, the diaphragm 70 can greatly improve the tolerance of the high-frequency pushing action of the cylindrical balance 502, thereby effectively extending the service life of the entire four-pressure diaphragm pump. In addition, since the diameter of the cylindrical balance 502 is increased, the area of the downward inclined surface 508 is also increased, so that the area of the bottom surface of the diaphragm sheet 70 which is in contact with the obliquely pulled state can be increased during the operation (as shown in FIG. 27). A shows), and increases the support of the rebound force Fs, thereby reducing the degree of influence of the diaphragm 70 on the rebound force Fs, and also prolonging the service life of the diaphragm 70.

As shown in FIG. 28 to FIG. 31, in the second embodiment of the present invention, "the structure of the balance of the four plenum diaphragm pump is improved", the cylindrical balance 502 can be changed from a cylindrical seat 511 and a pendulum. The wheel ring 521 is composed of a positioning flat 512 on the outer peripheral surface of the cylindrical seat 511, and a convex cylinder 513 is protruded from the top surface, and a concave hole is formed in the center of the top surface of the convex cylinder 513. 514; the balance ring 521 is sleeved on the cylindrical seat 511, and the outer peripheral surface thereof is disposed to be inclined toward the inner side surface 522, and the upper end hole 523 and the intermediate step are mutually penetrated in the direction from the center of the top surface to the bottom surface. The hole 524 and the lower hole 525 have a larger diameter than the outer diameter of the convex cylinder 513 in the cylindrical seat 511. The inner diameter of the middle hole 524 is the same as the outer diameter of the convex cylinder 513 in the cylindrical seat 511. The inner diameter of the hole 525 is the same as the outer diameter of the cylindrical seat 511, and the area from the upper step hole 523 to the inwardly inclined side surface 522 is set as a downward slope 526, and the balance ring 521 is placed on the cylindrical seat 511. Can be in convex cylinder 513 A positioning annular groove 515 is formed between the upper stepped hole 523 (as shown in FIGS. 30 and 31).

As shown in FIG. 32 to FIG. 35, after the balance ring 521 is engaged with the cylindrical seat 511, the four positioning convex ring blocks 76 on the bottom surface of the diaphragm piece 70 are respectively inserted into the four cylinders of the balance wheel holder 500. The positioning ring 502 of the balance wheel 502 is inserted into the stepped hole 81 of the piston push block 80 by the fixing screw 1 and passes through the central through hole 75 of the four piston actuating regions 74 of the diaphragm 70. The diaphragm piece 70 and the four-piston push block 80 are simultaneously screwed into the threaded holes 514 of the cylindrical seat 511 of the four-cylinder balance 502 in the balance wheel holder 500 (as shown in an enlarged view in FIG. 32); when the output of the motor 10 is output When the shaft 11 rotates, when the four cylindrical balance wheels 502 are rotated by the inclined eccentric cam 40 to push up the bottom surface of the diaphragm 70 of the piston actuation region 74, the upward force F thereof causes the convex ring block 76 to be positioned in the diaphragm 70. The diaphragm body between the outer ribs 71 produces an upwardly inclined state by the positioning annular groove 515 of the balance ring 521 of the cylindrical balance 502 to the downward slope of the inwardly inclined side surface 522. 526, can be completely flat contact at the same time and supported on the bottom surface of the diaphragm sheet 70 in the diagonally pulled state without squeezing the bottom surface of the diaphragm sheet 70 The phenomenon of 〞 (as shown in FIGS. 33 and 34), and the rebound force Fs generated by the diaphragm 70 is also greatly reduced (as shown by the arrow distribution of the rebound force Fs of each size in FIG. 34), The design structure of the inwardly inclined side surface 522 can still avoid the impact on the wall surface of the pumping head 60 to actuate the perforation 61 when the diameter of the cylindrical balance 502 is increased. Therefore, in addition to completely eliminating the lack of the squeezing flaw of the bottom surface of the diaphragm 70 in the conventional four plenum diaphragm pump, the rounded corner 57 of the cylindrical balance 502 (shown as an imaginary line in FIG. 35), After the diaphragm 70 is subjected to the upward force F, the rebound force Fs is synchronously reduced, so that the diaphragm 70 can greatly improve the tolerance of the cylindrical balance 502 to the high frequency pushing effect, thereby effectively extending the diaphragm 70. The service life of the entire four plenum diaphragm pump, and having the same effect as the second embodiment described above, the balance ring having the inwardly inclined side surface 522 and the downward slope 526 521, the feasibility of stripping must be considered in the production, so it can be made separately from the balance wheel holder 500, which can save the manufacturing cost, and the cylindrical seat 511 can be made integrally with the balance wheel holder 500, and then The two are combined into a cylindrical balance 502. Therefore, this structural design has the dual benefits of industrial mass production and overall manufacturing cost savings.

In summary, the invention adopts the simplest cylindrical balance wheel to improve the service life of the diaphragm in the four plenum diaphragm pump, and the service life of the entire four-pressure diaphragm pump is also increased. More than twice the original, very highly industrially usable and practical, and in line with the requirements of the patent, is to apply according to law.

50‧‧‧wheel seat

51‧‧‧balance bearing

52‧‧‧Cylindrical balance wheel

53‧‧‧ horizontal top surface

54‧‧‧Threaded holes

55‧‧‧ positioning ring groove

56‧‧‧Vertical side faces

58‧‧‧ downward slope

Claims (2)

A "four-pressurized diaphragm pump balance wheel structure improvement" includes: a motor; a motor front cover, which is embedded with a bearing in the center, and is inserted by the output shaft of the motor, and has a circle on the outer circumference. a convex ring, and a plurality of fixed perforations are provided on the inner edge surface and the outer edge surface of the upper convex ring; a tilting eccentric cam has a shaft hole penetrating through the center thereof and is sleeved on the output shaft of the motor; The wheel base has a pendulum wheel bearing embedded in the center of the bottom and is sleeved on the inclined eccentric cam. The top surface of the seat body is equidistantly spaced and arranged with four cylindrical balance wheels, and the horizontal top surface of each cylindrical balance wheel a threaded hole is defined in the recess, and a ring of positioning ring groove is further recessed on the periphery of the threaded hole; a pump head seat is sleeved on the upper convex ring of the motor front cover, and the top surface thereof is provided with four The actuating perforations are equally spaced and larger than the outer diameters of the four cylindrical balance wheels in the balance wheel seat, so that the four cylindrical balance wheels can be placed in the four actuating perforations, and the bottom surface is provided with a downward convex ring. The dimension of the lower convex ring is the same as that of the upper convex ring of the motor front cover, and is close to the outer circumference. The top surface is convex downward direction, and then several fixed perforations are provided; a diaphragm piece is placed on the top surface of the pump head seat, and is formed by semi-rigid elastic material, and the outermost peripheral edge is provided with two rings on the top surface. The outer ribs and the inner ribs are parallel to each other, and four ribs are connected to the inner ridge by the central position of the top surface, so that the four ribs and the inner rib are between There are four piston actuating zones spaced apart, and each piston actuating zone corresponds to the threaded hole position of the top surface of each cylindrical balance in the balance wheel seat, and each has a central perforation and is located at each central perforation. A ring positioning convex ring block is protruded from the bottom surface of the diaphragm piece; four piston pushing blocks are respectively placed in the four piston actuating regions of the diaphragm piece, and a stepped hole is formed through each piston push block, and the bottom surface of the diaphragm piece is four The positioning convex ring blocks are respectively inserted into the positioning ring grooves of the four cylindrical balance wheels in the balance wheel seat, and then inserted into the stepped holes of the piston pushing block by the fixing screws, and actuated through the four pistons in the diaphragm piece. After the central perforation of the zone, the diaphragm piece and the four-piston push block can be screwed together at the same time. Balance wheel seat four threaded hole wheel cylinder; a piston valve, based on a diaphragm disposed sleeve, an outer peripheral edge of the bottom side is provided with a downwardly projecting a ring-shaped rib, which can be inserted into a gap between the outer rib and the inner rib in the diaphragm, and a circular drain seat having a concave curved surface at a central position facing the pump head cover, and is disposed on the drain seat The center is provided with a positioning hole for a T-shaped anti-reverse rubber pad to be inserted and fixed, and four drainage holes are formed in each of the four regions formed by the positioning holes at an angle of 90 degrees. And on the outer surface of the drainage seat corresponding to the drainage holes of the four areas, four water inlets which are arranged at an angle of 90 degrees and whose openings are facing downward are respectively connected, and several water inlets are respectively arranged on each water inlet seat. a water inlet hole, and an inverted T-shaped piston piece is disposed in the center of each water inlet seat; and a pump head cover is disposed on the pump head seat, and the diaphragm piece and the piston valve body are covered, The edge surface is provided with a water inlet, a water outlet and a plurality of fixed perforations, and the bottom ring of the inner edge surface is provided with a stepped groove, and the outer edge of the composite surface of the diaphragm piece and the piston valve body can be superposed on each other. a stepped groove, and a ring of convex rings at the center of the inner edge surface; the feature is: the pendulum The diameter of each cylindrical balance in the seat is changed to be larger, but still smaller than the inner diameter of the working perforation in the pump head seat, and the side surfaces thereof are arranged to be inclined inwardly to the side surfaces, and each of the cylindrical balance wheels The region on the horizontal top surface that positions the annular groove to the inwardly inclined side surface is provided with a downward slope. As described in the first aspect of the patent application, "the structure of the balance of the four plenum diaphragm pump is improved", wherein each of the cylindrical balances is changed to be composed of a cylindrical seat and a balance ring, wherein a circumferential positioning surface of the cylindrical seat is provided with a positioning plane, and a convex cylinder is convexly protruded from the top surface, and a concave hole is formed in a central portion of the top surface of the convex cylinder; the balance ring is sleeved on the cylindrical seat The outer peripheral surface is formed to be inclined inwardly to the side surface, and the upper end hole, the middle step hole and the lower step hole are mutually penetrated in the direction of the bottom surface from the center of the top surface, wherein the upper hole has a larger aperture than the cylindrical seat The outer diameter of the convex cylinder, the inner diameter of the middle hole is the same as the outer diameter of the convex cylinder in the cylindrical seat, the inner diameter of the lower hole is the same as the outer diameter of the cylindrical seat, and the upper side hole is inclined to the inner side surface. The area is set to a downward slope, so that the balance ring is placed behind the cylindrical seat, and a positioning annular groove can be formed between the convex cylinder of the cylindrical seat and the upper hole of the balance ring.