CN218542553U - Pump head of booster pump, booster pump and water treatment facilities - Google Patents

Abstract

The application provides a pump head, diaphragm booster pump and water treatment facilities of diaphragm booster pump, the pump head includes: a transmission member including a drive shaft; the eccentric assembly is connected with the driving shaft and is driven by the driving shaft to rotate; the balance wheel assembly is connected with the eccentric assembly, and the rotation of the eccentric assembly drives the balance wheel assembly to swing along the radial direction of the driving shaft; the four rectangular pressurizing components are connected with the transmission component and are arranged oppositely in pairs along the axis of the driving shaft, each pressurizing component comprises a piston chamber, and at least one pressurizing cavity is arranged on the inner wall of the piston chamber; the diaphragm and the piston chamber are sealed to form at least one pressurizing cavity; the oscillation of the balance wheel assembly drives the diaphragm to deform in the radial direction of the drive shaft, so that the at least one pressurizing cavity expands or compresses in the radial direction. Through radial deformation of the diaphragm of the two pairs of rectangular pressurizing parts which are arranged in pairs, the flow is improved, and meanwhile, the manufacturing process is simplified; the transmission part can meet the static balance and the dynamic balance during operation, thereby further reducing the vibration.

Description

Pump head of booster pump, booster pump and water treatment facilities

Technical Field

The application relates to the technical field of water treatment, concretely relates to pump head, booster pump and water treatment facilities of booster pump.

Background

The diaphragm booster pump has the working principle that the periodic movement of the diaphragm causes volume change to drive the rubber valve to periodically close and open the water inlet and the water outlet on the valve seat, so that the boosting is realized.

As shown in fig. 1 and 2, the key components of a conventional diaphragm booster pump include a motor, an eccentric wheel, three balance wheels, a diaphragm divided into three piston actuating regions, three pistons, a piston chamber including three sets of water inlets and a set of water outlets, a three-inlet check valve, a drain check valve, a pump head cover including a water inlet and a drain, and a water inlet flow passage and a water drain flow passage which are separated from each other. Wherein, form former water cavity between pump head lid inlet channel and the piston room, form the high-pressure water cavity between pump head lid drainage runner and the piston room, form three independent pressure boost water cavity between piston room and the diaphragm.

When the motor rotates, the eccentric wheel can be driven to rotate. The balance wheels are limited not to rotate, so that the three balance wheels can only perform axial reciprocating motion in sequence, and the three piston motion areas of the diaphragm can perform synchronous axial expansion-compression motion by the axial reciprocating motion of the balance wheels. When the diaphragm piston moves towards the expansion direction, the water inlet check valve is opened, and the source water is sucked into the pressurized water cavity from the water inlet. When the diaphragm piston moves towards the compression direction, the drainage one-way valve is opened, pressurized water is pressed out and enters the high-pressure water cavity through the drainage hole, and is discharged out of the pump through the drainage hole of the pump head cover, so that required high-pressure water is provided.

The diaphragm booster pump has the following disadvantages: in the working process, the three balance wheels push the diaphragm in turn and continuously apply force in the same direction. When the rotating speed of the motor shaft reaches 700-1200rpm, the vibration generated by the alternate motion of the three balances is extremely large, so that great noise is generated. In addition, the diaphragm booster pump has a small flow rate. To increase the flow rate, the motor speed needs to be increased or the pump body needs to be increased in volume. However, increasing the motor speed can cause vibration and noise problems to be more serious, and the increased size can cause the booster pump to be difficult to install in cooperation with the existing equipment.

In order to solve the problem of vibration of the diaphragm of the above booster pump caused by axial force, a booster pump structure has been proposed in which a plurality of eccentric wheels are used to simultaneously apply opposite radial forces to a set of fan-shaped booster chambers, so as to reduce vibration and noise and increase flow rate by canceling the radial forces. However, in the manufacturing process of the fan-shaped pressurizing cavity structure, the difficulty that the mold opening process is complex, the manufacturing difficulty is high and the like exists, and the vibration cannot be completely eliminated.

Disclosure of Invention

In order to reduce the manufacturing degree of difficulty of the booster pump, further eliminate vibrations, the application provides a pump head, diaphragm booster pump and water treater of diaphragm booster pump.

According to a first aspect of the present application, there is provided a pump head of a diaphragm booster pump, the pump head comprising:

the transmission component comprises a transmission component and a transmission component,

a drive shaft;

the eccentric assembly is connected with the driving shaft and driven by the driving shaft to rotate;

the balance wheel assembly is connected with the eccentric assembly, and the rotation of the eccentric assembly drives the balance wheel assembly to swing along the radial direction of the driving shaft;

four rectangular pressurizing components connected with the transmission component and arranged along the axis of the driving shaft in a pairwise opposite way, wherein the pressurizing components comprise,

the piston chamber is provided with at least one pressurizing cavity on the inner wall;

a diaphragm enclosing the piston chamber to form the at least one booster cavity;

the oscillation of the balance wheel assembly drives the diaphragm to deform along the radial direction of the driving shaft, so that the at least one pressurizing cavity expands or compresses along the radial direction.

According to some embodiments of the present application, the eccentric assemblies are 180 ° out of phase during rotation, and the resulting eccentric forces cancel each other out and are moment balanced.

According to some embodiments of the present application, the eccentric assembly comprises a first eccentric, a second eccentric, and a third eccentric arranged in sequence along the drive shaft; the second eccentric is eccentric opposite to the first eccentric.

According to some embodiments of the application, the balance wheel assembly, during oscillation, has zero resultant of radial eccentric forces along the drive shaft and a resultant moment balance.

According to some embodiments of the application, the balance wheel assembly comprises:

the first balance wheel is connected with the first eccentric wheel;

the second balance wheel is connected with the second eccentric wheel;

a third balance wheel connected with the third eccentric wheel;

the third balance wheel and the first balance wheel swing in the same direction; the second balance wheel swings in the opposite direction to the first balance wheel.

According to some embodiments of the application, the at least one plenum comprises:

the first booster cavity is driven by the first balance wheel to deform the diaphragm so as to expand or compress the diaphragm in the radial direction;

the second pressurization cavity is driven by the second balance wheel to deform the diaphragm so as to radially expand or compress the diaphragm;

and the third pressurizing cavity is driven by the third balance wheel to deform the diaphragm so as to radially expand or compress the diaphragm.

According to some embodiments of the present application, the third plenum chamber and the first plenum chamber are simultaneously expanded or compressed; and the second pressurizing cavity and the first pressurizing cavity are compressed or expanded in opposite directions.

According to some embodiments of the present application, when the thinner portions of the first eccentric wheel and the third eccentric wheel rotate to the corresponding first balance wheel and the third balance wheel, the deformation regions of the diaphragm corresponding to the first balance wheel and the third balance wheel are in a near-axis position, and the volumes of the first pressurizing cavity and the third pressurizing cavity are maximum; the eccentric positions of the second eccentric wheel, the first eccentric wheel and the third eccentric wheel are opposite, meanwhile, the thinner part of the second eccentric wheel rotates to the position of the second balance wheel, the corresponding deformation area of the diaphragm is located at the position close to the axis, and the volume of the second pressurizing cavity is maximum.

According to some embodiments of the application, when the first eccentric wheel and the third eccentric wheel are eccentrically rotated to the corresponding first balance wheel and the third balance wheel, deformation areas of the diaphragm corresponding to the first balance wheel and the third balance wheel are in a far axis position, and the volumes of the first pressurizing cavity and the third pressurizing cavity are minimum; meanwhile, the thicker part of the second eccentric wheel rotates to the position of the second balance wheel, the corresponding deformation area of the diaphragm is positioned at the far axis position, and the volume of the second pressurizing cavity is the minimum.

According to some embodiments of the present application, the at least one pressurizing cavity of the four rectangular pressurizing members performs an expansion or compression motion in sequence.

According to some embodiments of the present application, the at least one pumping chamber completes one expansion and compression cycle per rotation of the drive shaft.

According to some embodiments of the application, the pump head further comprises:

the first end cover is arranged at one end of the transmission component;

the water inlet end is arranged on the first end cover;

and the water outlet end is arranged on the first end cover.

According to some embodiments of the application, the piston chamber further comprises:

the water inlet cavity is connected with the water inlet end;

and the water outlet cavity is connected with the water outlet end.

According to some embodiments of the present application, when the diaphragm expands in a radial direction of the drive shaft, the inlet check valve of the at least one pressurizing chamber opens, and source water is drawn into the at least one pressurizing chamber; when the water is compressed along the radial direction of the driving shaft, the water outlet one-way valve of the at least one pressurizing cavity is opened, and pressurized water is discharged.

According to another aspect of the present application, there is also provided a diaphragm booster pump comprising a pump head of the above-described diaphragm booster pump.

According to another aspect of the present application, there is also provided a water treatment apparatus including: the diaphragm booster pump is provided.

The pump head of the diaphragm booster pump provided by the application thoroughly changes axial deformation of the diaphragm into radial deformation, and the radial deformation of the diaphragm is used for realizing pressurization, so that the deformation area of the diaphragm is effectively increased, and the flow of the diaphragm booster pump is improved; on the basis, the structural forms of the piston chamber and the pressurizing cavity are further improved, the requirements on a die are greatly reduced, the manufacturing process is simplified, and the water inlet end and the water outlet end are arranged at one end of the pump head, so that the structure of a product is more compact; in addition, the three eccentric wheels and the three balance wheels are arranged, so that the pump head reaches a dynamic balance state of resultant moment balance, vibration is further reduced, and noise is reduced.

Drawings

In order to more clearly illustrate the technical solutions of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for a person skilled in the art to obtain other drawings based on these drawings without exceeding the protection scope of the present application.

Fig. 1 is a schematic view of a conventional diaphragm booster pump.

Fig. 2 is an exploded view of a conventional diaphragm booster pump.

Figure 3 is a schematic diagram of a membrane booster pump according to an example embodiment of the present application.

Figure 4 is an exploded view of a diaphragm booster pump according to an exemplary embodiment of the present application.

FIG. 5 is an exploded view of a transmission component according to an exemplary embodiment of the present application.

FIG. 6 is a schematic view of an eccentric assembly according to an exemplary embodiment of the present application.

Fig. 7 is a schematic view of a balance assembly according to an example embodiment of the present application.

FIG. 8 is an exploded view of a plenum member according to an exemplary embodiment of the present application.

FIG. 9 is a schematic view of a piston chamber according to an example embodiment of the present application.

FIG. 10 is a schematic view of a diaphragm according to an exemplary embodiment of the present application.

Figure 11 is a schematic view of an adapter according to an example embodiment of the present application.

Fig. 12 is a schematic view of a first end cap according to an example embodiment of the present application.

FIG. 13 is a schematic illustration of a substrate according to an example embodiment of the present application.

Figure 14 is a schematic diagram of a pump head of a diaphragm booster pump according to an example embodiment of the present application.

Figure 15 is an exploded view of a pump head of a diaphragm booster pump according to an exemplary embodiment of the present application.

FIG. 16 is a schematic view of a transmission assembly according to an exemplary embodiment of the present application.

FIG. 17 is a schematic illustration of an eccentric assembly according to an exemplary embodiment of the present application.

Fig. 18 is a schematic view of a balance assembly according to an example embodiment of the present application.

Fig. 19 is a schematic diagram of a balance according to an example embodiment of the present application.

Fig. 20 is a schematic diagram of a balance according to an example embodiment of the present application.

FIG. 21 is a schematic view of a diaphragm according to an exemplary embodiment of the present application.

FIG. 22 is an exploded view of a plenum member according to an example embodiment of the present application.

FIG. 23 is a schematic view of a slider according to an example embodiment of the present application.

FIG. 24 is a schematic view of a slider according to an example embodiment of the present application.

FIG. 25 is a schematic view of a diaphragm to slider connection configuration according to an exemplary embodiment of the present application.

Fig. 26 is a schematic view of a water inlet and outlet structure according to an exemplary embodiment of the present application.

FIG. 27 is a cross-sectional view of a water access structure according to an example embodiment of the present application.

Fig. 28 is a schematic view of a first end cap according to an example embodiment of the present application.

Detailed Description

Example embodiments will now be described more fully hereinafter with reference to the accompanying drawings. Example embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of example embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar parts, and a repetitive description thereof will be omitted.

Furthermore, the described features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a thorough understanding of embodiments of the application. One skilled in the relevant art will recognize, however, that the embodiments of the present application can be practiced without one or more of the specific details, or with other methods, components, devices, steps, and so forth. In other instances, well-known methods, devices, implementations, or operations have not been shown or described in detail to avoid obscuring aspects of the application.

It will be understood that, although the terms first, second, etc. may be used herein to describe various components, these components should not be limited by these terms. These terms are used to distinguish one element from another. Thus, a first component discussed below could be termed a second component without departing from the teachings of the present concepts. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Those skilled in the art will appreciate that the drawings are merely schematic illustrations of example embodiments, which may not be to scale. The blocks or flows in the drawings are not necessarily required to practice the present application and therefore should not be used to limit the scope of the present application.

In order to solve the problem of vibration caused by axial force on a diaphragm of the existing booster pump, a booster pump structure which adopts a plurality of eccentric wheels to apply opposite radial force to a booster cavity simultaneously appears, and vibration and noise are reduced by mutual offset of the radial force. The inventor finds that in the structure, the piston chamber and the pressurizing cavity are in a pair of fan-shaped blocks, so that the requirement on a die is high, the die opening process is complex, and the manufacturing process difficulty is high; and the vibrations cannot be completely eliminated.

Therefore, the pump head of the novel diaphragm booster pump is provided, on one hand, the difficulty of the manufacturing process is reduced through structural improvement, and the product structure is more compact; on the other hand, on the basis of the improvement of the product structure, the dynamic balance state is achieved through a plurality of radial forces, so that the vibration is thoroughly eliminated. The technical solution of the present application will be described in detail below with reference to the accompanying drawings.

FIG. 3 is a schematic diagram of a membrane booster pump according to an exemplary embodiment of the present application; figure 4 is an exploded view of a diaphragm booster pump according to an exemplary embodiment of the present application.

As shown in fig. 3 and 4, the pump head 1000 of the diaphragm booster pump provided by the present application includes a transmission member 100, a base 200, four rectangular pressurizing members 300, and a first end cap 400. The base 200 is a structural main body of the pump head 1000, the transmission component 100 is arranged inside the base 200, and the four rectangular pressurizing components 300 are arranged around the base 200; the first cap 400 is disposed at one end of the base 200.

Compared with the pump heads of the conventional membrane booster pumps in fig. 1 and 2, the pump head 1000 of the membrane booster pump provided by the present application is structurally improved from a cylindrical shape to a rectangular structure. The four rectangular pressurizing members 300 are arranged opposite to each other two by two along the axis of the driving member 100 (i.e., the axis of the pump head 1000). As can be seen from fig. 4, the basic shape of the pressurizing member 300 is rectangular, compared with the annular or fan-shaped pressurizing member, the requirement on the mold is reduced in the manufacturing process, the mold opening process is simpler, and the manufacturing process is simpler.

FIG. 5 is an exploded view of a transmission component according to an exemplary embodiment of the present application; FIG. 6 is a schematic illustration of an eccentric assembly according to an exemplary embodiment of the present application; fig. 7 is a schematic view of a balance assembly according to an example embodiment of the present application.

As shown in fig. 5, the transmission assembly 100 includes a drive shaft 110, an eccentric assembly 120, a balance assembly, a set of bearings 140, and a second end cap 150. Wherein the eccentric assembly 120 may be a set of eccentric sleeves connected to the driving shaft 110 to rotate with the driving shaft 100. As shown in fig. 6, the eccentric assembly 120 includes a first eccentric 121, a second eccentric 122, and a third eccentric 123 arranged in sequence along the driving shaft 110. The third eccentric wheel 123 and the first eccentric wheel 121 have the same eccentricity; the second eccentric 122 is eccentric opposite to the first eccentric 121, i.e. 180 ° out of phase. Because the phase difference between the second eccentric wheel 122 and the first eccentric wheel 121 and the third eccentric wheel 122 is 180 degrees during the rotation of the eccentric assembly 120, the generated eccentric forces are mutually counteracted and are in moment balance, and the vibration can be further eliminated.

As shown in fig. 5 and 7, the balance assembly 130 is connected to the eccentric assembly 120 through a set of bearings 140, and the rotation of the eccentric assembly 120 drives the balance assembly 130 to swing along the radial direction of the driving shaft 110. The balance assembly 130 includes, in sequence along the drive shaft 110, a first balance 131, a second balance 132, and a third balance 133. Wherein, the first balance 131 is connected with the first eccentric wheel 121; a second balance 132 is connected to the second eccentric 122; a third balance 133 is connected to said third eccentric 123. The third balance 133 and the first balance 131 swing in the same direction; the second balance 132 oscillates in the opposite direction to the first balance 131, i.e. 180 ° out of phase. According to an example embodiment of the present application, first balance 131 and third balance 133 may be small balances and second balance 132 may be a large balance. During the oscillation of the oscillating assembly 130, the phase difference between the second balance 132 and the first balance 131 and the third balance 132 is 180 °, so that the generated radial eccentric forces are mutually counteracted and are in moment balance, and further the vibration can be eliminated.

The phase difference of the eccentric components is 180 degrees in the rotating process, namely the phase difference is 180 degrees, the generated eccentric forces are mutually counteracted, and the moment is balanced.

The eccentric assembly comprises a first eccentric wheel, a second eccentric wheel and a third eccentric wheel which are sequentially arranged along the driving shaft; namely, the eccentric distances are equal, and the eccentric directions are the same; the second eccentric wheel and the first eccentric wheel are opposite in eccentricity, namely, the eccentric distances are equal, and the eccentric directions are opposite.

And in the swinging process of the balance wheel assembly, the resultant force of the radial eccentric force of the driving shaft is zero and the resultant moment is balanced.

The balance wheel assembly includes:

the first balance wheel is connected with the first eccentric wheel;

the second balance wheel is connected with the second eccentric wheel;

a third balance wheel connected with the third eccentric wheel;

the third balance wheel and the first balance wheel swing in the same direction; the second balance wheel and the first balance wheel swing in opposite directions; i.e. the second balance oscillates in the same direction as the first balance, with a phase angle different by 180 °.

As shown in fig. 7, a set of swing arms 134 is fixed to each of the first balance 131, the second balance 132, and the third balance 133. In the oscillating process of the balance wheel assembly 130, the oscillating arm 134 is connected with the diaphragm through the adapter in the pressurizing component to drive the diaphragm to deform in the radial direction, so that the expansion or compression is performed.

FIG. 8 is an exploded view of a plenum member according to an exemplary embodiment of the present application; FIG. 9 is a schematic view of a piston chamber according to an exemplary embodiment of the present application; FIG. 10 is a schematic view of a diaphragm according to an exemplary embodiment of the present application; figure 11 is a schematic diagram of an adapter according to an example embodiment of the present application.

As shown in fig. 8, each pressurizing member 300 includes a piston chamber 310, a diaphragm 320, an adapter 330, a packing 340, a housing 350, a set of inlet check valves 360, and a set of outlet check valves 370. Wherein at least one pressurizing cavity is provided on the inner wall of the piston chamber 310. The diaphragm 320 and the piston chamber 310 are closed to form the at least one pressurizing cavity. The housing 350 and the sealing ring 340 are used to receive and seal the piston chamber 310. Diaphragm 320 is coupled to the balance assembly by adapter 330. The oscillation of the balance assembly drives diaphragm 320 through adapter 330 to deform in the radial direction of the drive shaft, expanding or compressing at least one pumping chamber in the radial direction. The piston chamber 310 and the diaphragm 320 may be integrated or assembled.

As shown in fig. 9, the piston chamber 310 is provided with a water inlet chamber 311, a water outlet chamber 312, and at least one pressurizing chamber, and is formed by closely adhering a diaphragm to the inner wall of the piston chamber 310. According to an example embodiment of the present application, the at least one plenum includes a first plenum 313, a second plenum 314, and a third plenum 315. The first pressurizing chamber 313 and the third pressurizing chamber 315 are small pressurizing chambers, and the second pressurizing chamber 314 is a large pressurizing chamber. An inlet chamber 311 and an outlet chamber 312 are provided at one end of the piston chamber 310. Each pressurizing cavity is provided with a water inlet 316 and a water outlet 317 which are respectively provided with a water inlet check valve 360 and a water outlet check valve 370.

As shown in fig. 10, diaphragm 320 includes a first deformation zone 323, a second deformation zone 324, and a third deformation zone 325, which correspond to first plenum 313, second plenum 314, and third plenum 315, respectively, of fig. 9. A set of protrusions 326 is provided on each deformation zone of the diaphragm 320. The projection 326 is connected to the swing arm of the balance via an adapter. As a result, first pressurizing chamber 313 in fig. 9 is radially expanded or compressed by first wobbler 131 in fig. 7 driving first deformation region 323 of diaphragm 320 in fig. 10 to deform; the second pressurizing cavity 314 is driven by the second balance 132 in fig. 7 to deform the second deformation region 324 of the diaphragm 320 in fig. 10 so as to radially expand or compress; third pumping chamber 315 is radially expanded or compressed by third wobbler 133 of fig. 7 driving third deformation region 325 of diaphragm 320 of fig. 10 to deform.

As shown in fig. 8 and 11, the adapter 330 includes a first small adapter, a large adapter, and a second small adapter. The first small adapter is connected at one end to the projection 326 of the first deformation zone 323 of the diaphragm 320 in fig. 10 and at the other end to the oscillating arm 134 of the first balance 131 in fig. 7; one end of the large adapter is connected with the bulge 326 of the second deformation zone 324 of the diaphragm 320 in fig. 10, and the other end is connected with the swing arm 134 of the second balance 132 in fig. 7; the second small adapter is connected at one end to the projection 326 of the third deformation zone 325 of the diaphragm 320 in fig. 10 and at the other end to the oscillating arm 134 of the third balance 133 in fig. 7.

After the transmission member 300 of fig. 5 and the 4 pressurizing members 300 of fig. 8 are assembled, the pressurizing members 300 are arranged opposite to each other two by two along the axis of the rotating shaft 110. The oppositely arranged pressurizing cavities form a pair. The first pumping cavity 313 of the piston chamber 310 may be a first small pumping cavity, the second pumping cavity 314 may be a large pumping cavity, and the third pumping cavity 315 may be a second small pumping cavity. The third pressurizing cavity 315 and the first pressurizing cavity 313 expand or compress synchronously; second pumping chamber 314 compresses or expands in opposition to first pumping chamber 133. For example: when the first small pressurizing cavity and the second small pressurizing cavity expand, the large pressurizing cavity compresses; when the first small pressurizing cavity and the second small pressurizing cavity are compressed, the large pressurizing cavity expands.

FIG. 12 is a schematic view of a first end cap according to an example embodiment of the present application; FIG. 13 is a schematic illustration of a substrate according to an example embodiment of the present application.

As shown in fig. 12, the first end cap 410 is provided with a water inlet end 411 and a water outlet end 412. The end surface of the base 200 is provided with a first water outlet 201 and a first water inlet 202, which are assembled to connect with a water outlet end 412 and a water inlet end 411 of the first end cap 410, respectively. The four sides of the base 200 are respectively provided with a second water inlet 203 and a second water outlet 204, which are respectively connected with the water inlet cavity and the water outlet cavity of the piston chamber after being assembled, thereby forming a water inlet channel and a water outlet channel. In the working process, raw water enters from the water inlet end 411 of the first end cover 410 and forms a water inlet flow channel through the first water inlet 202 and the second water inlet 203 on the base body 200; then enters the water inlet cavity 311 through the water inlet of the piston chamber 310 in FIG. 9, and enters the pressurizing cavity 313 and/or the pressurizing cavity 314 and/or the pressurizing cavity 315 through the water inlet of the pressurizing cavity provided with the water inlet check valve; the pressurized water enters the water outlet cavity 312 from the water outlet of the pressurizing cavity provided with the water outlet check valve de. The pressurized water flows into the outlet flow channel formed by the second outlet hole 204 of the base 200 and the first outlet 201 through the outlet of the outlet cavity 312, and finally is discharged from the outlet end 412 of the first end cap 410. The application provides a pump head will intake the water end and go out the water end and set up in the one end of pump for product structure compactness more.

As shown in fig. 13, a first mounting hole 210, a second mounting hole 220, and a third mounting hole 230 are respectively formed on four side surfaces of the base 200, and are respectively used for mounting a first adapter, a second adapter, and a third adapter of the pressurizing member. The base 200 further includes a mounting base 240 disposed at an opposite end of the first end cap. When the pump head is assembled, the transmission component is installed inside the base body, and is connected and fixed with the second end cap of the transmission component through the installation seat 240.

Referring to fig. 3 and 4, in the operation process of the assembled pump head 1000, the eccentric rotation of the eccentric assembly 120 drives the balance wheel assembly 130 to perform radial reciprocating motion, the balance wheel assembly is connected to the diaphragm 320 through the adaptor 330, and the reciprocating motion of the balance wheel assembly 130 makes the deformation area of the diaphragm 320 perform radial expansion motion or compression motion. Eccentric assemblies 120 cancel each other out and are moment balanced during rotation, and resultant radial eccentric force generated by eccentric motion of balance assembly 130 is zero and is moment balanced. Each pressurizing cavity of the four rectangular pressurizing members 300 sequentially performs an expansion or compression movement. Each pumping chamber completes one expansion and compression cycle per rotation of drive shaft 110. The first balance 131, the third balance 133, and the second balance 132 move away from the axial center of the drive shaft 110 or close to the axial center at the same time, and the forces generated in the radial direction cancel each other out, so that the resultant force becomes zero.

For example, when the thin portions of the first eccentric wheel 121 and the third eccentric wheel 123 in fig. 6 rotate to the corresponding first balance wheel 131 and the third balance wheel 133 in fig. 4, the deformation regions of the diaphragm 320 corresponding to the first balance wheel 131 and the third balance wheel 133 are in the near-axis position, and the volumes of the first pressurizing cavity and the third pressurizing cavity are maximum; the eccentric position of the second eccentric wheel 122 is opposite to that of the first eccentric wheel 121 and the third eccentric wheel 123, and meanwhile, the thinner part of the second eccentric wheel 122 rotates to the position of the second balance wheel 132, the corresponding deformation region of the diaphragm 320 is in a near-axis position, and the volume of the second pressurizing cavity is maximum.

Similarly, when the thick portions of the first eccentric wheel 121 and the third eccentric wheel 123 rotate to the corresponding first balance 131 and the third balance 133, the deformation regions of the diaphragm 320 corresponding to the first balance 131 and the third balance 133 are located at the positions far from the axis, and the volumes of the first pressurizing cavity and the third pressurizing cavity are minimum. Meanwhile, the thicker part of the second eccentric wheel 122 rotates to the position of the second balance wheel 132, the deformation area of the corresponding diaphragm 320 is at a far axis position, and the volume of the second pressurizing cavity is minimum.

When the diaphragm 320 expands in the radial direction of the driving shaft 110, the water inlet check valve of the at least one pressurizing chamber is opened, and the source water is sucked into the at least one pressurizing chamber; when compressed in the radial direction of the driving shaft 110, the outlet check valve of the at least one pressurizing chamber is opened, and pressurized water is discharged.

According to another aspect of the present application, there is provided a diaphragm booster pump comprising the pump head of the above-described diaphragm booster pump.

According to another aspect of the application, a water treatment device is also provided, which comprises the diaphragm booster pump.

The application provides a diaphragm booster pump's pump head passes through eccentric subassembly rotation and drives the balance wheel and produce radial reciprocating motion to make diaphragm deformation direction be radial. Compare with traditional diaphragm booster pump, under the unchangeable condition of pump body volume and motor speed, the radial deformation of diaphragm can effectively increase diaphragm deformation area, increases the volume variable in pressure-increasing cavity to improve the flow of diaphragm booster pump. Secondly, the pump head of the diaphragm booster pump provided by the application is further improved on the structural forms of the piston chamber and the booster cavity, so that the requirements on a die are greatly reduced, and the manufacturing process is simplified. In addition, eccentric forces of the eccentric assemblies are mutually offset and balanced in moment in the rotating process, the first balance wheel, the third small balance wheel and the second balance wheel simultaneously deviate from the axis of the motor shaft or move close to the axis simultaneously, the forces applied in the radial direction are mutually offset, the resultant force is zero and the resultant moment is balanced, the vibration and the noise are greatly reduced, and the relatively silent effect can be achieved. In the pump head of the diaphragm booster pump that this application provided, improve the both ends of intaking end and play water end by the pump for setting up in the one end of pump for the compactness that the product structure is more.

Another embodiment of the present invention is a variation of the invention in some details as compared to embodiment 1, wherein the driving unit of the pump head comprises the eccentric assembly, the driving assembly, a bearing, and a sliding block semi-fixed to the balance assembly.

The balance wheel is provided with a guide rail, the sliding block is provided with a sliding groove, and the guide rail is in clearance fit with the sliding groove, so that the sliding block and the balance wheel can slide relatively along the direction of the guide rail.

The diaphragm is provided with a plurality of diaphragm reversing groups, and the diaphragm reversing is connected with the slider reversing groove.

The sliding block comprises a first sliding block, a second sliding block and a third sliding block, the first sliding block is connected with a first reverse-buckling group of the diaphragm in a reverse buckling mode, a sliding groove of the first sliding block is connected with a first balance rail, the second sliding block is connected with a second reverse-buckling group of the diaphragm in a reverse buckling mode, a sliding groove of the second sliding block is connected with a second balance rail, the third sliding block is connected with a third reverse-buckling group of the diaphragm in a reverse buckling mode, and a sliding groove of the third sliding block is connected with a third balance rail.

The diaphragm reverse-buckling group is matched with the slider reverse-buckling groove, and the diaphragm upper fixing groove is matched with the slider upper fixing pin to increase the relative movement force between the diaphragm and the slider.

And the two pressurizing cavity groups symmetrically arranged by taking the central point of the piston chamber as a center form a pair, namely, the pair of pressurizing cavities are arranged, and the central lines of the pair of pressurizing cavity groups are on the same diameter line of the piston chamber.

At least 2 pairs, preferably 3 pairs or 6 pairs of the pressurizing cavity groups are subjected to expansion or compression movement.

The pressurizing cavity group comprises a first small pressurizing cavity corresponding to the first balance wheel, a large pressurizing cavity corresponding to the second balance wheel and a second small pressurizing cavity corresponding to the third balance wheel. The first small pressurizing cavity and the second small pressurizing cavity are synchronously expanded or compressed; when the first small pressurizing cavity and the second small pressurizing cavity expand, the large pressurizing cavity compresses; when the first small pressurizing cavity and the second small pressurizing cavity are compressed, the large pressurizing cavity expands, particularly, the sum of the compressed volumes of the first small pressurizing cavity and the second small pressurizing cavity is equal to the expanded volume of the large pressurizing cavity, and conversely, the sum of the expanded volumes of the first small pressurizing cavity and the second small pressurizing cavity is equal to the compressed volume of the large pressurizing cavity.

The contact part of the diaphragm and the sliding block is a diaphragm deformation area, and the diaphragm deformation area deforms.

The balance wheel of the transmission assembly rotates eccentrically to drive the sliding block to reciprocate in the radial direction, the sliding block and the balance wheel slide relatively, and the sliding block drives the diaphragm to deform in the radial direction, so that the pressurizing cavity expands or compresses in the radial direction.

And when the motor shaft rotates for one circle, each pressurizing cavity of the pressurizing cavity group completes one expansion and compression cycle.

The first balance wheel, the third balance wheel and the second balance wheel simultaneously deviate from the axle center of the motor shaft or simultaneously move close to the axle center, the stress in the radial direction is mutually counteracted, and the resultant force is zero.

When the thinner parts of the first eccentric wheel and the third eccentric wheel rotate to the balance wheels linked with the first eccentric wheel and the third eccentric wheel, the balance wheels push the corresponding diaphragm deformation area to be positioned at the position close to the center point of the piston chamber, and the volume of the small pressurizing cavity corresponding to the small balance wheels is the largest; the eccentric positions of the second eccentric wheel, the first eccentric wheel and the second eccentric wheel are opposite, when the thinner part of the second eccentric wheel rotates to the position of the second balance wheel linked with the second eccentric wheel, the position of the deformation area of the corresponding diaphragm is close to the central point of the piston chamber, and the volume of the pressurizing cavity is maximum.

When the first eccentric wheel and the third eccentric wheel rotate to the first balance wheel and the second balance wheel which are linked with the first eccentric wheel and the third eccentric wheel in a thick position, a diaphragm deformation area corresponding to the balance wheel is positioned at a position far away from the center point of the piston chamber, and the volume of the pressurizing cavity is minimum; meanwhile, when the thicker part of the second eccentric wheel rotates to the position of the second balance wheel linked with the second eccentric wheel, the corresponding diaphragm deformation area is positioned at the position far away from the center point of the piston chamber, and the volume of the pressurizing cavity is the minimum.

The membrane sheet comprises at least one membrane sheet or a plurality of membrane sheet assemblies, and the membrane sheets are formed by splicing a plurality of membrane sheet assemblies.

When the diaphragm moves towards the expansion direction, the water inlet check valve is opened, the water outlet check valve is closed, and source water is sucked into the pressurization cavity; when the diaphragm moves towards the compression direction, the water inlet check valve is closed, the water outlet check valve is opened, and pressurized water is discharged.

The piston chamber includes at least one piston chamber assembly, and a plurality of piston chamber assemblies are assembled to form a piston chamber.

The diaphragm or the piston chamber is integral or assembled.

The diaphragm is tightly attached to the inner wall of the piston chamber and is sealed to form a water outlet cavity, the pressurizing cavity and a water inlet cavity.

The diaphragm reverse-buckling group is matched with the slider reverse-buckling groove, so that the diaphragm and the slider are relatively fixed, the diaphragm upper fixing groove is matched with the fixing pin on the slider, and the relative motion force between the diaphragm and the slider is increased, so that the diaphragm and the slider are not easy to rub with each other;

the guide rail on the balance wheel is matched with the sliding groove on the sliding block, so that the sliding block and the balance wheel can slide relatively along the direction of the guide rail.

Compared with the traditional diaphragm booster pump, the invention maximally utilizes the volume of the pump head, obtains the largest diaphragm movement area under the condition that the volume of the pump body is not changed, and increases the volume variable of the working cavity when the reciprocating amplitudes of the diaphragms are the same, thereby improving the flow rate of the diaphragm booster pump;

the eccentric components offset each other in eccentric force and balance moment in the rotation process, the first balance wheel, the third balance wheel and the second balance wheel simultaneously deviate from the axle center of the motor shaft or move close to the axle center, the radial stress is offset each other, the resultant force is zero and the resultant moment is balanced, the vibration and the noise are greatly reduced, and the effect of relative silence can be achieved.

The buffer cavity is arranged in the pressurization cavity and is a part of space in the pressurization cavity, the space is enlarged along with the increase of pressure, the pressure is reduced and reduced, when the diaphragm moves upwards, the pressurization cavity is reduced, the pressure in the pressurization cavity is increased, the size of the buffer cavity is increased due to the increase of the pressure, and therefore the increase of the pressure in the pressurization cavity is delayed.

Evenly set up a plurality of cushion chambers on the diaphragm, when working chamber pressure increases in the twinkling of an eye, the cushion chamber volume grow slows down working chamber pressure increase trend, and when working chamber pressure reduces in the twinkling of an eye, the cushion chamber volume reduces, slows down working chamber pressure reduction trend for working chamber pressure is gentler in the course of the work, and then the play water pressure pulsation reduces, reduces the influence of play water pressure pulsation to system's pipeline.

The sliding block slides on the balance wheel, so that tangential motion generated by eccentric motion of the balance wheel is eliminated, the diaphragm linearly reciprocates along the radial direction, the service life of the diaphragm is prolonged, friction loss is reduced, and the efficiency of the water pump is improved.

The motor shaft drives the eccentric component to eccentrically rotate, the eccentric rotation of the eccentric component drives the transmission component to eccentrically move, the transmission component is connected with the diaphragm through the sliding block, the sliding block and the balance wheel can slide mutually, the eccentric movement of the transmission component enables the sliding block to reciprocate along the diameter direction of the rotating shaft, and the sliding block drives the diaphragm deformation area to radially expand or compress. Eccentric forces of the eccentric assemblies are mutually offset and balanced in moment in the rotating process, resultant eccentric force generated by eccentric motion of the transmission assembly is zero and balanced in resultant moment, so that the pressurizing cavity is radially expanded or compressed, when the deformation area of the diaphragm moves towards the expansion direction, the water inlet one-way valve is opened, and source water is sucked into the pressurizing cavity from the water inlet cavity through the water inlet; when the deformation area of the diaphragm moves towards the compression direction, the water outlet one-way valve is opened, pressurized water is pressed out, enters the water outlet cavity from the water outlet and is discharged from the water outlet cavity.

Specifically, in another embodiment of the present invention, fig. 14 is a schematic view of a diaphragm booster pump according to the present embodiment, and fig. 15 is an exploded view of the diaphragm booster pump according to the present embodiment.

As shown in fig. 14, a pump head 1000 of a diaphragm booster pump of the pump embodiment includes a driving part 100, a base 200, four rectangular pressurizing parts 300, and a first end cap 400. The base 200 is a structural body of the pump head 1000, the transmission component 100 is disposed inside the base 200, and the four rectangular pressurizing components 300 are disposed around the base 200; the first end cap 400 is disposed at one end of the base 200.

Compared with the embodiment shown in fig. 3 and 4, the present embodiment provides another embodiment of the structure of the eccentric assembly 120, the balance assembly 130, the diaphragm 320 and the adapter 330 in the diaphragm booster pump head 1000.

As shown in fig. 16, drive assembly 100 is shown to include a drive shaft 110, an eccentric assembly 120, a wobbler assembly 130, a bearing assembly 140, and a second end cap 150. In contrast to fig. 6, the eccentric assembly 120 in this embodiment is three eccentric wheels independent of each other. As shown in fig. 17, the eccentric assembly 120 includes a first eccentric 121, a second eccentric 122, and a third eccentric 123.

As shown in fig. 18, balance assembly 130 includes a first balance 131, a second balance 132, and a third balance 133.

As shown in fig. 19, the first wobbler 131 includes a sliding rail 1311 and a sliding surface 1312. The third balance 133 has the same structure as the balance 131.

As shown in fig. 20, the second balance 132 includes a slide rail 1321 and a slide surface 1322.

As shown in fig. 21, the diaphragm 320 includes a water inlet 321, a water outlet 322, a first deformation region 323, a second deformation region 324, a third deformation region 325, a buffer cavity 327, a first inverse buckle group 3291, a second inverse buckle group 3292, a third inverse buckle group 3293, a first limit groove 3281, a second limit groove 3282, and a third limit groove 3283.

As shown in fig. 22, the slider 330 includes a first slider 331, a second slider 332, and a third slider 333.

As shown in fig. 23, the first slider 331 includes a stopper pin 3311, a undercut 3312, a slide groove 3313, and a slide surface 3314. The third slider 333 and the first slider 331 have the same structure.

As shown in fig. 24, the second slider 332 includes a stopper pin 3321, a reversed groove 3322, a sliding groove 3323, and a sliding surface 3324.

As shown in FIG. 25, first set of barbs 3291 on diaphragm 320 snap into barbs 3312 on first slider 331, securing diaphragm 320 and first slider 331 to one another. The first fixing groove 3291 of the diaphragm 320 is in interference fit with the stopper pin 3311 of the first slider 331, so as to increase the coupling force between the diaphragm 320 and the first slider 331. Similarly, the second reverse-buckling group 3292 on the diaphragm 320 is buckled with the reverse-buckling groove 3322 on the second sliding block 332, and the second fixing groove 3292 on the diaphragm 320 is in interference fit with the limit pin 3321 on the second sliding block 332; the third reverse-buckling group 3293 on the diaphragm 320 is buckled with the reverse-buckling groove 3332 on the third sliding block 333, and the third fixing groove 3293 on the diaphragm 320 is in interference fit with the limit pin 3331 on the second sliding block 333.

As shown in fig. 25, the slide groove 3313 of the first slider 331 and the slide rail 1311 of the first balance 131 are in clearance fit with each other, and the slide surface 3314 of the first slider 331 and the slide surface 1312 of the first balance 131 contact each other. So that the first slider 331 and the first balance 131 can move relative to each other along the sliding rail 1311. Similarly, the second slider 332 and the third slider 333 are respectively connected to the second balance wheel 132 and the third balance wheel 133 in the same manner.

As shown in fig. 14, the improved structure has the advantages that the sliding block 330 slides on the balance 130, so that the tangential motion generated by the eccentric motion of the balance 130 is eliminated, the diaphragm 320 linearly reciprocates along the radial direction, the service life of the diaphragm is prolonged, the friction loss is reduced, and the efficiency of the water pump is improved.

As shown in fig. 26 and 27, the valve seat 310, the pump housing 350, and the seal 340 form a first inlet chamber 351 and a first outlet chamber 352. The diaphragm 320 and the valve seat 310 form a working chamber 314. Source water enters the inlet 411 and simultaneously enters the four inlet 2021 2022 2023 2024 via the second inlet chamber 414, wherein the source water entering the inlet 2021 exits the 2031 hole through the inlet flow path and then enters the 311 inlet hole, and the water entering the 311 inlet hole enters the first inlet chamber 351. When the diaphragm 320 moves downward, the volume of the working chamber 314 increases, the check valve 360 opens, the check valve 370 closes, and water in the first water inlet chamber 351 flows into the working chamber 314, thereby completing the water suction operation. When the diaphragm 320 moves upward, the volume of the working chamber 314 decreases, the check valve 360 closes, the check valve 370 opens, the water in the working chamber 314 is discharged to the first water outlet chamber 352, the first water outlet chamber 352 is connected with the water outlet hole 312, the water outlet hole 2041 is communicated with the water outlet hole 2011, and the water in the working chamber 312 is discharged to the water outlet hole 2011 through the water outlet hole. The pressurized water in the first water outlet cavities in the four directions is collected to the second water outlet cavity 415 through the water outlet holes 2011, 2012, 2013 and 2014, and the high-pressure water in the second water outlet cavity 415 is discharged out of the pump head through the water outlet 412, so that pressurization is completed. The water inlets and the water outlets of the pressurizing cavities distributed in four directions are connected in parallel by water paths. And a static end face sealing structure is adopted to divide the water inlet cavity and the water outlet cavity. And the number of the connecting joints between the cavities is reduced, so that the risk of leakage of pipeline connection is reduced. And through establishing the mode at the pump body in with the water route, reduce the volume that the water route occupy by a wide margin for the pump head is compacter, simplifies connecting line, reduces the volume, reduces and leaks the risk.

As shown in FIG. 21, the diaphragm 320 has three deformation regions, including a first deformation region 323, a second deformation region 324, and a third deformation region 325. Each deformation zone is filled with a buffer chamber 327. The buffer chamber 327 has the function of reducing the peak pressure value of the working chamber 314 and increasing the peak-to-valley pressure value of the working chamber 314, so as to reduce the pressure pulsation at the water outlet 412, thereby greatly reducing the noise.

The working principle of the buffer chamber 327 is as shown in fig. 27, the buffer chamber 327 is disposed in the working chamber 314 and is a part of the space in the working chamber 314, and the volume of the part of the space is increased as the pressure in the working chamber 314 is increased and is decreased as the pressure in the working chamber 314 is decreased. When the diaphragm 320 starts to move upward from the lowest point, the volume of the working chamber 314 decreases, the pressure in the working chamber 314 increases instantaneously, and the volume of the buffer chamber 327 increases due to the increase in pressure, thereby absorbing part of the pressure energy, and thus reducing the peak pressure in the working chamber 314. When the diaphragm 320 starts to move downwards from the highest point, the volume of the working chamber 314 increases, the pressure in the working chamber 314 decreases instantaneously, the volume of the buffer chamber 327 decreases due to the decrease of the pressure, and the stored pressure energy is released, so that the valley pressure in the working chamber 314 is increased, and the pressure change amplitude in the working chamber 314 is reduced.

The embodiments of the present application are described in detail above. The principle and the implementation of the present application are explained herein by applying specific examples, and the above description of the embodiments is only used to help understand the technical solutions and the core ideas of the present application. Therefore, the person skilled in the art should, according to the idea of the present application, change or modify the embodiments and applications of the present application based on the scope of protection of the present application. In view of the above, the description should not be taken as limiting the application.

Claims (17)

1. A pump head for a booster pump, the pump head comprising:

the transmission component comprises a transmission component and a transmission component,

a drive shaft;

the eccentric assembly is connected with the driving shaft and driven by the driving shaft to rotate;

the balance wheel assembly is connected with the eccentric assembly, and the rotation of the eccentric assembly drives the balance wheel assembly to swing along the radial direction of the driving shaft;

the inner wall of the piston chamber is provided with a pressurizing cavity;

a diaphragm enclosing the piston chamber to form the pressurizing cavity;

the swing of the balance wheel assembly drives the diaphragm to deform along the radial direction of the driving shaft, so that the pressurization cavity expands or compresses along the radial direction.

2. A pump head according to claim 1, wherein the eccentric assemblies are 180 ° out of phase during rotation, the resulting eccentric forces cancelling out and moment-balancing.

3. A pump head of a booster pump as claimed in claim 2,

the eccentric assembly comprises a first eccentric wheel, a second eccentric wheel and a third eccentric wheel which are sequentially arranged along the driving shaft; the eccentricity of the third eccentric wheel is consistent with that of the first eccentric wheel; the second eccentric is eccentric opposite to the first eccentric.

4. A pump head according to claim 3, wherein the balance assembly has zero resultant of the eccentric forces in the radial direction of the drive shaft during oscillation and is moment-balanced.

5. A pump head for a booster pump according to claim 3, wherein the balance assembly comprises:

the first balance wheel is connected with the first eccentric wheel;

the second balance wheel is connected with the second eccentric wheel;

a third balance wheel connected with the third eccentric wheel;

the third balance wheel and the first balance wheel swing in the same direction;

the second balance wheel swings in the opposite direction to the first balance wheel.

6. A pump head for a booster pump as claimed in claim 5, wherein at least one booster chamber comprises:

the first balance wheel drives the diaphragm to deform so as to radially expand or compress;

the second booster cavity is driven by the second balance wheel to deform the diaphragm so as to radially expand or compress the diaphragm;

and the third pressurizing cavity is driven by the third balance wheel to deform the diaphragm so as to expand or compress in the radial direction.

7. A pump head for a booster pump according to claim 6,

the third pressurizing cavity and the first pressurizing cavity are synchronously expanded or compressed;

and the second pressurizing cavity and the first pressurizing cavity are compressed or expanded in opposite directions.

8. A pump head for a booster pump as claimed in claim 1, wherein a buffer chamber is provided within the pumping chamber.

9. A pump head according to claim 6, wherein when the first and third eccentrics are rotated to the first and third wobbles, deformation regions of the diaphragm corresponding to the first and third wobbles are located at a position close to the axial line, and volumes of the first and third pressurizing chambers are maximized; the eccentric positions of the second eccentric wheel, the first eccentric wheel and the third eccentric wheel are opposite, meanwhile, the thinner part of the second eccentric wheel rotates to the position of the second balance wheel, the corresponding deformation area of the diaphragm is located at the position close to the axis, and the volume of the second pressurizing cavity is maximum.

10. A pump head of a booster pump according to claim 6, wherein when the first and third eccentrics are rotated to the corresponding first and third wobblers at a thickness, deformation regions of the diaphragm corresponding to the first and third wobblers are located at a position of a far axis, and a volume of the first and third pumping chambers is minimized; meanwhile, the thicker part of the second eccentric wheel rotates to the position of the second balance wheel, the corresponding deformation area of the diaphragm is positioned at the far axis position, and the volume of the second pressurizing cavity is the minimum.

11. A pump head according to claim 6, wherein the at least one pumping chamber undergoes sequential expansion or compression movements.

12. A pump head according to claim 1, wherein at least one of said pumping chambers completes one expansion and compression cycle per revolution of said drive shaft.

13. A pumphead for a booster pump as claimed in claim 1, further comprising:

the first end cover is arranged at one end of the transmission component;

the water inlet end is arranged on the first end cover;

and the water outlet end is arranged on the first end cover.

14. A pump head for a booster pump as claimed in claim 13, wherein the piston chamber further comprises:

the water inlet cavity is connected with the water inlet end;

and the water outlet cavity is connected with the water outlet end.

15. A pump head for a booster pump according to claim 14, wherein, as said diaphragm expands in the radial direction of said drive shaft, the inlet check valve of at least one of said pumping chambers opens and source water is drawn into said at least one of said pumping chambers; when the water is compressed along the radial direction of the driving shaft, the water outlet one-way valve of at least one pressurizing cavity is opened, and pressurized water is discharged.

16. A booster pump, comprising:

a pumphead for a booster pump as claimed in any one of claims 1 to 15.

17. A water treatment device, comprising:

the booster pump of claim 16.

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