CN111734610A - Diaphragm pump and its pump head structure - Google Patents

Abstract

The invention discloses a diaphragm pump and a pump head structure thereof, wherein the pump head structure comprises: the diaphragm is provided with a first surface matched with the transmission head and a second surface matched with the valve seat; the second surface is provided with a plurality of wading portions which can contact with fluid, a pressurizing cavity is formed between each wading portion and the valve seat, and the area ratio of the wading portions to the diaphragm is as follows: 50 to 70 percent. The diaphragm pump and the pump head structure thereof can improve parameters such as water outlet flow, working efficiency and the like of the diaphragm pump under the condition of ensuring that the volume of the diaphragm pump is unchanged and the structure durability is good, thereby meeting the requirements of users on high performance, low cost, low noise, small size and the like of the diaphragm pump.

Description

Diaphragm pump and its pump head structure

technical field

The invention relates to the technical field of diaphragm pumps, in particular to a diaphragm pump and a pump head structure thereof.

Background technique

Diaphragm pumps are mechanical structures that deliver liquids or pressurize liquids through a diaphragm. The existing diaphragm pump can use a reciprocating drive member to drive the diaphragm to deform to achieve the purpose of sucking liquid; it can also be driven by a driving member such as a nutating disc or a swinging disc to drive the diaphragm to deform to achieve the purpose of suctioning liquid. Diaphragm pumps are widely used in water purification and other industries.

At present, the diaphragm pumps provided by manufacturers are largely standardized into several fixed models. Different types of diaphragm pumps correspond to parameters such as predetermined water flow and fixed volume. In general, the larger the water flow of the diaphragm pump, the larger its volume.

However, in the case of a certain internal space of the water purification system, it can only install a diaphragm pump with a predetermined water outlet flow. If you want to install a diaphragm pump with higher water flow and other working parameters than the same model in a limited space, it is necessary to further improve the existing diaphragm pump.

SUMMARY OF THE INVENTION

The purpose of the present invention is to provide a diaphragm pump and its pump head structure, which can improve parameters such as the water outlet flow rate and working efficiency of the diaphragm pump under the condition that the volume of the diaphragm pump is kept unchanged and the structure durability is good, so as to satisfy the user's requirements for the diaphragm pump. The demand for high performance, low cost, low noise, and miniaturization of the pump.

Above-mentioned purpose of the present invention can adopt following technical scheme to realize:

A pump head structure, comprising: a drive head, a diaphragm and a valve seat arranged in sequence along the direction of a motor output shaft, the diaphragm has a first surface matched with the drive head and a second surface matched with the valve seat. Two surfaces; the second surface is provided with a plurality of wading parts that can be in contact with the fluid, and a pressurized cavity is respectively formed between each of the water wading parts and the valve seat, and the water wading parts occupy The area ratio of the diaphragm is: 50%-70%.

Further, the diaphragm includes a sealing portion that is arranged between the edge of the diaphragm and the water wading portion and is matched with the valve seat and is not less than a predetermined size.

Further, the second surface of the diaphragm is provided with a reinforcing rib on the sealing portion between two adjacent water wading portions.

Further, the edge of the wading portion is an arc transition.

Further, the shape enclosed by the edge of the wading portion includes any one of the following: oval, irregular and quasi-circular.

Further, the transmission head is provided with a balance wheel matching the number of the wading parts, and the area ratio of the balance wheel to the wading part is 70% to 90%, wherein the pendulum wheel The area ratio of the wheel to the water wading part is the projected area ratio of the balance wheel and the water wading part on the same reference plane along the direction of the motor output shaft.

Further, the cross section of the balance wheel is oval.

Further, the ratio of the minimum distance from the outermost cavity wall of the boosting cavity to the periphery of the pump head to the diameter of the pump head is 4% to 6%.

Further, the ratio of the minimum distance between the cavity walls of the two adjacent pressurizing chambers to the diameter of the pump head is 8% to 10%.

Further, the number of the pressurizing chambers is three, and the three pressurizing chambers are evenly distributed around the motor output shaft.

Further, the cross-sectional shape of the pressurizing chamber is an ellipse or an irregular quasi-circular shape.

Further, the first surface of the diaphragm abuts on the pump cover, the transmission head is provided with a balance wheel matching the number of the wading parts, and the pump cover is provided with a hole for wearing Describe the opening of the balance wheel.

Further, the opening and the balance wheel are in clearance fit, and the clearance between the two is between 0.8 mm and 1.5 mm.

Further, the area occupied by the balance wheel is 42% to 60% of the cross-sectional area of the entire pump head.

Further, the openings are elliptical holes.

Further, the area ratio of the water wading part to the diaphragm is: the projected area ratio of the water wading part and the diaphragm on the same reference plane along the direction of the motor output shaft.

A diaphragm pump, comprising: the pump head structure described in any one of the above, and a motor that provides driving force for the transmission head.

Further, the rotational speed of the motor is between 1200RPM and 1800RPM, the output torque is between 0.4N.M and 0.8N.M, and the flow rate of the diaphragm pump is between 4LPM and 8LPM.

From the technical solutions provided by the above embodiments of the present application, it can be seen that by optimizing the diaphragm in the pump head structure and the structure of the matching transmission head and valve seat, the water wading in the diaphragm, which can affect the efficiency of the diaphragm pump, is improved. The area ratio of the pump head is maximized under the premise of ensuring the total volume of the diaphragm pump, long-term reliability and safety, etc. Improve the utilization rate of the volume in the booster chamber), thereby improving the water flow and working efficiency of the diaphragm pump.

The experimental data verification shows that: under the condition of the same motor speed, the flow rate of the diaphragm pump using the pump head structure provided by the application is significantly larger than that of the diaphragm pump using the existing pump head structure at the same motor speed; Under the flow rate, the diaphragm pump using the pump head structure provided by the present application can effectively reduce the motor speed, thereby reducing the reciprocating fatigue wear of the diaphragm, thereby improving the life of the diaphragm pump and reducing the noise of the diaphragm pump.

With reference to the following description and drawings, specific embodiments of the present application are disclosed in detail, indicating the manner in which the principles of the present application may be employed. It should be understood that the embodiments of the present application are not thereby limited in scope. Embodiments of the present application include many changes, modifications and equivalents.

Features described and/or illustrated for one embodiment may be used in the same or similar manner in one or more other embodiments, in combination with, or instead of features in other embodiments .

It should be emphasized that the term "comprising/comprising" when used herein refers to the presence of a feature, integer, step or component, but does not exclude the presence or addition of one or more other features, integers, steps or components.

Description of drawings

1 is a schematic structural diagram of a pump head structure in an embodiment of the present application;

2 is an exploded view of a pump head structure in an embodiment of the present application;

3 is a schematic structural diagram of a middle diaphragm of a pump head structure in an embodiment of the present application;

4 is a front view of the middle diaphragm of the pump head structure in an embodiment of the present application;

5 is a top view of the middle diaphragm of the pump head structure in an embodiment of the present application;

6 is a rear view of the middle diaphragm of the pump head structure in an embodiment of the present application;

7 is a schematic structural diagram of a middle valve seat of a pump head structure in an embodiment of the present application;

8 is a front view of a middle valve seat of a pump head structure in an embodiment of the present application;

9 is a rear view of the middle valve seat of the pump head structure in an embodiment of the present application;

10 is a schematic structural diagram of a middle drive head of a pump head structure in an embodiment of the present application;

11 is a top view of a middle drive head of a pump head structure in an embodiment of the present application;

12 is a schematic structural diagram of a middle pump cover of a pump head structure in an embodiment of the present application;

13 is a top view of the middle pump cover of the pump head structure in an embodiment of the present application;

14 is a schematic diagram of the whole machine structure of the diaphragm pump provided in the embodiment of the present application;

FIG. 15 is a schematic diagram of the comparison between the outlet water pressure and the outlet water flow rate of the diaphragm pump provided in the embodiment of the present application and the existing diaphragm pump under the premise of the same rotational speed and the same eccentric wheel.

Description of reference numbers:

1. Diaphragm; 11. First surface; 111. Matching part; 12. Second surface; 121. Water wading part; 122. Sealing part; 123. Reinforcing rib; 2. Valve seat; Water outlet; 20, pressurization chamber; 3, transmission head; 31, balance wheel; 4, pump cover; 41, opening; 5, motor; 6, upper cover; 7, eccentric wheel; 8, bearing.

Detailed ways

The technical solutions of the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that these embodiments are only used to illustrate the present invention and not to limit the scope of the present invention. Various equivalent modifications of the invention are intended to fall within the scope defined by the claims appended hereto.

It should be noted that when an element is referred to as being "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for the purpose of illustration only and do not represent the only embodiment.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the technical field to which this application belongs. The terms used herein in the specification of the present application are for the purpose of describing particular embodiments only, and are not intended to limit the present application. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

In order to meet the needs of users for high performance, low cost, low noise, and miniaturization of the diaphragm pump, this application improves the internal structure of the diaphragm pump on the premise of ensuring that the volume of the diaphragm pump remains unchanged and the structure is durable. The working parameters of the diaphragm pump greatly improve the water flow and work efficiency.

An embodiment of the present application provides a pump head structure, which is mainly used in a diaphragm pump.

1 to 14, the working principle of the diaphragm pump is as follows: when the output shaft of the motor 5 rotates, it will drive the inclined eccentric 7 to rotate; a bearing 8 is arranged between the inclined eccentric 7 and the transmission head 3, and the eccentric Because the wheel 7 has a predetermined eccentric angle, when it rotates, it can drive the balance wheel 31 on the transmission head 3 to reciprocate up and down in sequence along the direction of the output shaft of the motor 5; the wading part 121 on the diaphragm 1 is also synchronously moved up Push up or pull down to produce repeated up and down displacement. Specifically, when the balance wheel 31 of the transmission head 3 moves downward, the water wading part 121 of the diaphragm 1 and the piston push block (not shown in the figure) are pulled down synchronously, so that the piston plate of the valve seat 2 is pushed open, and the tap water It can enter into the pressurization chamber 20 through the water inlet hole on the valve seat 2; when the balance wheel 31 of the transmission head 3 moves upward, the wading part 121 and the piston of the diaphragm 1 are also pushed up to the top simultaneously, and the pressure is increased. The water in the cavity 20 is squeezed to increase the water pressure to a predetermined pressure range; the boosted high-pressure water can push the non-return rubber pad on the water outlet 22 on the valve seat 2 away, and the high-pressure water passes through the water outlet. The water outlet of the part 22 enters the high pressure water chamber.

Please refer to FIG. 3 to FIG. 6 , the pump head structure includes: a transmission head 3 , a diaphragm 1 and a valve seat 2 arranged in sequence along the direction of the output shaft of the motor 5 . The diaphragm 1 has a first surface 11 matched with the drive head 3 and a second surface 12 matched with the valve seat 2 . The second surface 12 is provided with a plurality of wading portions 121 that can be in contact with the fluid. A pressurizing chamber 20 is respectively formed between each of the wading portions 121 and the valve seat 2 . The area ratio of the wading portion 121 to the diaphragm 1 is 50%-70%.

In this embodiment, the diaphragm 1 has a first surface 11 that can cooperate with the drive head 3 of the diaphragm pump and a second surface 12 that can cooperate with the valve seat 2 of the diaphragm pump. Wherein, the second surface 12 is provided with a plurality of wading parts 121 that can be in contact with the fluid. The fluid mainly varies according to different application scenarios of the diaphragm pump, which is not specifically limited in this application. For example, when a diaphragm pump is used in a water purification system, the fluid may be water. The first surface 11 is provided with a matching portion 111 , which is used for positioning with the transmission head 3 . The driving force of the transmission head 3 received at the matching part 111 is transmitted to the corresponding components in the valve seat 2 through the wading part 121 , so that the corresponding components in the valve seat 2 can be driven by the transmission Head 3 is driven synchronously.

Please refer to FIG. 7 to FIG. 9 , in this embodiment, a pressurizing chamber 20 can be respectively formed between each of the water wading portions 121 and the valve seat 2 . Specifically, the valve seat 2 may be provided with a plurality of water inlet portions 21 equal in number to the water wading portions 121 , and a water outlet portion 22 that can communicate with the water inlet portions 21 . Wherein, the water inlet portion 21 may cooperate with the water wading portion 121 to form the pressurizing chamber 20 .

Specifically, the number of the pressurizing chambers 20 may be three, and the three pressurizing chambers 20 are evenly distributed around the output shaft of the motor 5 . The number of the boosting chambers 20 is preferably 3. On the one hand, the smaller the number of the boosting chambers 20, the more favorable it is to increase the area ratio of the boosting chambers 20 to the pump head; on the other hand, the 20 boosting chambers The smaller the number, the less the superimposed number of mutually independent supercharging chambers 20, and the smaller the total failure probability, on the premise that the failure probability of each supercharging chamber 20 is equal. The boosting chamber 20 is the core structure of the pump head structure, and the smaller the failure probability of the boosting chamber 20 is, the more beneficial it is to ensure the reliability of the pump head structure. The area ratio of the boosting chamber 20 to the pump head is specifically: the projected area ratio of the boosting chamber 20 and the pump head on the same reference plane along the direction of the output shaft of the motor 5 . Of course, the number of the pressurizing chambers 20 may also be four or more, and the plurality of pressurizing chambers 20 may be evenly distributed around the output shaft. Specifically, this application will not discuss them here.

Wherein, since the diaphragm 1 needs to be deformed to a certain extent when it is in direct contact with the transmission head 3, the material of the diaphragm 1 can be elastic plastic, rubber or other materials to meet the deformation requirements. Each wading portion 121 has a relatively closed outer contour. When sharp corners appear on the diaphragm 1, the diaphragm 1 made of the elastic material is prone to failure at the sharp corners. In order to ensure the reliability of the diaphragm 1 during use and prevent the diaphragm 1 from being damaged at sharp corners, the edge of the outer contour of the wading portion 121 is an arc-shaped transition.

Specifically, the shape enclosed by the edge of the wading portion 121 includes any one of the following: ellipse, irregular quasi-circle. Certainly, the shape surrounded by the edge of the wading portion 121 , that is, the outer contour of the wading portion 121 may also be other arc-shaped transition shapes, such as arc-shaped transition fan shapes and the like.

In the present application, the area ratio of the water wading portion 121 to the diaphragm 1 is between 50% and 70%. It should be noted that: since the water wading part 121 and the diaphragm 1 are in a three-dimensional shape, the area ratio of the water wading part 121 to the diaphragm 1 can be specifically: the water wading part 121 and the diaphragm 1 are along the The projected area ratio of the output shaft direction of the motor 5 on the same reference plane.

On the whole, the area ratio of the water wading portion 121 occupied by the diaphragm 1 is larger than that of the existing water wading portion 121 having a circular outer contour. When the area ratio of the wading part 121 to the diaphragm 1 is less than 50%, the flow characteristic of the diaphragm pump is low; when the area ratio of the wading part 121 to the diaphragm 1 is higher than 70%, the reliability of the diaphragm pump Performance (including life, strength, sealing, etc.) will decrease.

In the embodiment of the application, by optimizing the structure of the diaphragm 1 in the pump head structure and the matching structure of the transmission head 3 and the valve seat 2, the wading part in the diaphragm 1 that can affect the efficiency of the diaphragm pump is improved. The area ratio of 121 maximizes the volume utilization rate of the pump head structure under the premise of ensuring the total volume, long-term reliability and safety of the diaphragm pump, thereby improving the water flow and working efficiency of the diaphragm pump.

The area ratio of the water wading portion 121 to the diaphragm 1 is preferably selected on the premise of ensuring the overall structural strength and sealing performance. Please refer to FIG. 3 to FIG. 6 , the diaphragm 1 includes a sealing portion 122 , which is disposed between the edge of the diaphragm 1 and the water wading portion 121 and is matched with the valve seat 2 and is not smaller than a predetermined size.

Specifically, when the wading part 121 of the diaphragm 1 is matched with the valve seat 2 , the other parts of the diaphragm 1 are mainly used to form the above-mentioned sealing part 122 except the wading part 121 used to form the pressurizing chamber 20 . . Further, in order to ensure that the diaphragm 1 has a certain strength, the second surface 12 of the diaphragm 1 may be provided with a reinforcing rib 123 on the sealing part 122 between two adjacent water wading parts 121 .

Due to the existence of the eccentric angle θ of the eccentric wheel 7, the projected area of the booster cavity 20 and the water wading portion 121 along the output shaft of the motor 5 has the following relationship: the projected area of the booster cavity 20 along the output shaft of the motor 5 S1=projected area S2×cosθ of the water wading portion 121 along the output axis direction of the motor 5 . That is to say, the projected area of the boosting chamber 20 in the direction of the output shaft of the motor 5 corresponds to the projected area of the wading portion 121 in the direction of the output shaft of the motor 5 . The larger the projected area of the water wading portion 121 in the direction of the output shaft of the motor 5 is, the correspondingly the larger the projected area of the booster cavity 20 in the direction of the output shaft of the motor 5 is. When the area ratio of the water wading portion 121 to the diaphragm 1 is increased, the area ratio of the booster cavity 20 is also increased. When the area ratio of the boosting chamber 20 is increased, the volume of water pumped into the boosting chamber 20 at a time can be increased, thereby improving the unit flow rate and working efficiency of the diaphragm pump.

In some embodiments of this specification, on the premise that the size of the pump head remains unchanged, in order to increase the area ratio of the boosting chamber 20 as much as possible, the cross-sectional shape of the boosting chamber 20 is oval or irregular. of circular shape. Wherein, the area ratio of the boosting chamber 20 can be determined by the projection of the boosting chamber 20 and the pump head on the same reference plane along the direction of the output shaft of the motor 5 . As shown in FIG. 1 , the main part of the pressurizing chamber 20 may be formed by the water inlet part 21 of the valve body. Correspondingly, the water inlet 21 is provided with an oval or irregular circular hole.

In the following embodiments, the cross-sectional shape of the pressurizing chamber 20 is elliptical as an example for description. For other shapes of the pressurizing chamber 20, the elliptical pressurizing chamber 20 can be referred to by analogy, and the application will not describe them one by one. Expand the description.

In one embodiment, the ratio of the minimum distance from the outermost cavity wall of the boosting chamber 20 to the periphery of the pump head to the diameter of the pump head is 4% to 6%. The ratio of the minimum distance between the chamber walls of two adjacent boosting chambers 20 to the diameter of the pump head is 8% to 10%.

The first surface 11 of the diaphragm 1 is also provided with a pump cover 4 that cooperates with the upper cover 6 to limit the position of the diaphragm 1 . Specifically, the outer edge of the first surface 11 of the diaphragm 1 abuts on the pump cover 4 , and the sealing portion 122 of the second surface 12 of the diaphragm 1 is in sealing fit with the valve seat 2 . In order to ensure the tightness, structural strength and clearance installation requirements of the drive head 3, the outermost cavity wall of the booster cavity 20 (the position where the cavity wall of the booster cavity 20 is closest to the periphery of the pump head) reaches the periphery of the pump head (the pump head The circumference corresponding to the diameter) needs to meet a predetermined minimum distance. Specifically, the minimum distance can be matched with the model of the diaphragm pump. Generally, the larger the diameter of the pump head of the diaphragm pump, the larger the minimum distance.

For example, for a diaphragm pump with a pump head diameter of 76 mm (millimeters), the minimum distance from the outermost cavity wall of the boosting chamber 20 to the periphery of the pump head is about 3.37 mm. Wherein, the ratio of the minimum distance (3.37 mm) from the outermost cavity wall of the boosting chamber 20 to the periphery of the pump head to the diameter of the pump head (76 mm) is 4.43%. The minimum distance mainly considers the tightness requirements of the pump head at the diaphragm 1 and the assembly clearance requirements between the transmission head 3 and the pump cover 4 . Among them, the swing wheel of the transmission head 3 will reciprocate axially along the direction of the output shaft during use. In order to ensure that the transmission head 3 does not interfere with the pump cover 4 during use, the transmission head 3 and the pump cover 4 There needs to be at least 0.95mm of space between them.

In order to ensure the requirements of tightness and strength, a predetermined minimum distance needs to be satisfied between the chamber walls of two adjacent pressurizing chambers 20 . Specifically, the minimum distance can be matched with the model of the diaphragm pump. Generally, the larger the diameter of the pump head of the diaphragm pump, the larger the minimum distance. For example, for a diaphragm pump with a pump head diameter of 76 mm (mm), the minimum distance is about 6.5 mm, and the minimum distance (6.5 mm) between the chamber walls of two adjacent booster chambers 20 is related to the pump head diameter (76 mm) The ratio is 8.55%.

The applicant found that: when the ratio of the minimum distance from the outermost cavity wall of the pressurizing chamber 20 to the periphery of the pump head to the diameter of the pump head is 4% to 6%, the difference between the two adjacent pressurizing chambers 20 When the ratio of the minimum distance between the cavity walls to the diameter of the pump head is 8% to 10%, it is possible to maximize the expansion of the booster cavity 20 at the output of the motor 5 on the premise of ensuring the overall strength and sealing of the structure. The projected area in the axial direction. That is, the area ratio of the boosting chamber 20 is increased. When the area ratio of the boosting chamber 20 is increased, the volume of the boosting chamber 20 can be increased, which is beneficial to improve the unit flow rate and working efficiency of the booster pump.

Hereinafter, the shape enclosed by the edge of the wading portion 121 is the area ratio of the diaphragm 1 occupied by the ellipse (hereinafter referred to as the area ratio of the ellipse), which is different from the area occupied by the existing circular wading portion 121 of the diaphragm 1 . The area ratio (referred to as the ratio of circular area in the following calculation) is used for comparison.

A: The radius of the long semi-axis at the contact between the pump cover and the diaphragm (wading part), take 14.75mm;

B: The radius of the short semi-axis at the contact between the pump cover and the diaphragm (wading part), take 17mm;

T: the number of booster chambers, take 3;

r: the radius of the contact between the pump cover and the diaphragm (wading part), take 13.25mm;

T: the number of booster chambers, take 3;

It can be seen from the comparison between the above-mentioned oval area ratio and the existing circular area ratio: the oval area ratio provided by the present application is much larger than the existing circular area ratio. After the area ratio of the diaphragm 1 is increased, the area ratio of the booster chamber 20 is increased. When the area ratio of the boosting chamber 20 is increased, the volume of the boosting chamber 20 is increased, which is beneficial to improve the unit flow rate and the working efficiency of the booster pump. That is to say, the pump head structure provided by the present application can help improve the unit flow rate of the diaphragm pump on the premise that the volume of the diaphragm pump remains unchanged, thereby improving the working efficiency of the diaphragm pump.

When the area ratio of the diaphragm pump is within a reasonable range, it can ensure that the total volume of the diaphragm pump remains unchanged and the long-term reliable and safe operation of the diaphragm pump can maximize the use of the volume in the pump head structure and increase the volume of the booster chamber 20. , so as to improve the working efficiency of the diaphragm pump. In this embodiment, the area ratio of the pressurizing chamber 20 may be between 70% and 90%. When the area ratio of the booster chamber 20 is too small, for example, the area ratio of the booster chamber 20 of the existing diaphragm pump is usually less than 60%, the flow characteristic corresponding to the booster pump is poor at this time; When the area ratio of the pressure chamber 20 is greater than 90%, the sealing type and structural reliability of the diaphragm pump may be affected.

Please refer to FIG. 10 to FIG. 11 , the area of the wading portion 121 of the diaphragm 1 also has a matching relationship with the area of the balance wheel 31 of the transmission head 3 . Under the premise that the outer contour areas of the diaphragm 1 and the transmission head 3 remain unchanged, when the area of the wading part 121 of the diaphragm 1 increases, the area of the balance wheel 31 of the transmission head 3 also increases accordingly. When the two cooperate, the transmission head The larger the effective area of the balance wheel 31 acting on the wading portion 121 of the diaphragm 1 is, the more beneficial it is to improve the volume utilization rate of the booster chamber 20, thereby improving the unit flow rate and working efficiency of the diaphragm pump.

In one embodiment, the transmission head 3 is provided with a balance wheel 31 matching the number of the wading parts 121 , and the area ratio of the balance wheel 31 to the area of the wading part 121 is 70 % to 90%. The area ratio of the balance wheel 31 to the water wading part 121 is the projected area ratio of the balance wheel 31 and the water wading part 121 on the same reference plane along the output shaft direction of the motor 5 .

In a specific embodiment, taking the balance wheel 31 as an example with an elliptical cross-section, the degree of improvement in unit flow rate and working efficiency of the diaphragm pump compared to the existing diaphragm pump is illustrated as an example.

Existing diaphragm pump unit flow:

The meaning of each letter is as shown in the figure above:

Among them, ψ is the angle of the eccentric wheel, which is taken as 3.5°;

R1 is _20.5mm ; R2 is _11.75mm ; _R3 is 15mm;

The unit flow of the diaphragm pump provided by this application:

The new letters have the following meanings:

a: The radius of the long half shaft of the transmission head, take 15.15mm; b: The radius of the short half shaft of the transmission head, take 12.25mm;

A: The radius of the long half shaft of the pump cover, take 14.75mm; B: The radius of the short half shaft of the pump cover, take 17mm;

On the whole, the working efficiency of the diaphragm pump provided by the present application can be improved by about 38.9% compared with the existing diaphragm pump.

Please refer to FIG. 15 , which is a schematic diagram comparing the water outlet pressure and the water outlet flow between the diaphragm pump provided in the embodiment of the application and the conventional diaphragm pump under the premise of the same rotational speed and the same eccentric wheel 7 . On the premise of the same rotational speed of the motor 5 and the same eccentric wheel 7, the working efficiency of the diaphragm pump provided by the present application has been significantly improved compared with the traditional diaphragm pump.

In addition, please refer to Table 1, which is a comparison table of test data between the diaphragm pump with the pump head structure provided by the present application and the traditional diaphragm pump. The variables during the test are only "different motor speeds", everything else is the same.

Table 1

It can also be clearly seen from Table 1 that for a diaphragm pump of 1000G (gallons), under the same rotation speed of the motor 5, using the diaphragm pump with the pump head structure provided by the present application, under the same rotation speed of the motor 5, its flow rate Compared with the diaphragm pump with the traditional pump head structure, it is significantly larger. Under the same flow rate, the diaphragm pump using the pump head structure provided by the present application can effectively reduce the rotational speed of the motor 5, thereby reducing the reciprocating fatigue wear of the diaphragm 1, thereby improving the life of the diaphragm pump and reducing the noise of the diaphragm pump.

12 and 13, in one embodiment, the first surface 11 of the diaphragm 1 abuts on the pump cover 4, and the transmission head 3 is provided with a number of wading parts 121 corresponding to the number For the matching balance wheel 31 , the pump cover 4 is provided with an opening 41 for passing the balance wheel 31 .

In this embodiment, the pump cover 4 is mainly used for positioning the diaphragm 1 in cooperation with the upper cover 6 and the valve seat 2 . The pump cover 4 is provided with an opening 41 for passing through the balance wheel 31 of the transmission head 3 . There is clearance fit between the balance wheel 31 of the transmission head 3 and the opening 41 of the pump cover 4 . Specifically, the mating gap between the two can be between 0.8 mm and 1.5 mm.

The shape of the opening 41 can be matched with the cross section of the balance wheel 31 . When the cross section of the balance wheel 31 is oval, the opening 41 is an oval hole. The balance wheel 31 is projected along the direction of the output shaft of the motor 5, and the ratio of the projected area of the balance wheel 31 in the direction of the output shaft of the motor 5 (the transmission area) to the cross-sectional area of the pump head is 42% to 60% between. Under the condition that the cross-sectional area of the pump head is the same, the transmission area of the balance wheel 31 provided by the present application is much higher than that of the existing diaphragm pump. When the transmission area of the balance wheel 31 is increased, a larger area of the wading part 121 can be pushed to participate in the reciprocating action, which is beneficial to improve the utilization rate of the volume of the booster chamber 20, thereby improving the water outlet flow and working efficiency of the diaphragm pump.

Taking the actual data as an example, when the diameter of the diaphragm pump is 76mm, the cross-sectional area of the pump head is: 4534mm ² . The radius of the long semi-axis of the balance wheel 31 using the pump head structure of the present application is 15.15mm, the short radius is 12.25mm, and the sum of the transmission area of the balance wheel 31 is: 2150mm ² . The ratio of the transmission area of the balance wheel 31 to the cross-sectional area of the pump head is 47.42%, which is greatly improved compared to the ratio of the transmission area to the cross-sectional area of the pump head in the prior art.

Based on the pump head structure provided in the above embodiments, the present application also provides a diaphragm pump, the diaphragm pump includes: the pump head structure described in any of the above embodiments, and a driving force for the transmission head 3 . Motor 5.

Since the diaphragm pump provided in the present application is provided with the pump head structure described in the above embodiments, the technical effect that can be achieved by the above pump head structure can be achieved.

Specifically, for the diaphragm pump provided with the pump head structure described in the above embodiment, the rotational speed of the motor 5 is between 1200RPM (revolution per minute) and 1800RPM, and the output torque is between 0.4N.M (N.M) and 0.8N.M Between, the flow rate of the diaphragm pump is between: 4LPM (liters per minute)～8LPM.

Any numerical value recited herein includes all values of the lower value and the upper value in one unit increments from the lower value to the upper value, there being a separation of at least two units between any lower value and any higher value That's it. For example, if the number of components or process variables (eg, temperature, pressure, time, etc.) are stated to have values from 1 to 90, preferably from 20 to 80, more preferably from 30 to 70, the intent is to illustrate that the The specification also explicitly lists values such as 15 to 85, 22 to 68, 43 to 51, 30 to 32, and the like. For values less than 1, one unit is appropriately considered to be 0.0001, 0.001, 0.01, 0.1. These are merely examples of what is intended to be express, and all possible combinations of numerical values recited between the lowest value and the highest value are considered to be expressly set forth in this specification in a similar fashion.

Unless otherwise stated, all ranges include the endpoints and all numbers between the endpoints. "About" or "approximately" used with a range applies to both endpoints of the range. Thus, "about 20 to 30" is intended to cover "about 20 to about 30," including at least the indicated endpoints.

All articles and references disclosed, including patent applications and publications, are hereby incorporated by reference for all purposes. The term "consisting essentially of" describing a combination shall include the identified element, ingredient, component or step as well as other elements, components, components or steps that do not materially affect the essential novel characteristics of the combination. Use of the terms "comprising" or "comprising" to describe combinations of elements, ingredients, components or steps herein also contemplates embodiments consisting essentially of those elements, ingredients, components or steps. By use of the term "may" herein, it is intended to indicate that "may" include any described attributes that are optional.

A plurality of elements, components, components or steps can be provided by a single integrated element, component, component or step. Alternatively, a single integrated element, component, component or step may be divided into separate multiple elements, components, components or steps. The disclosure of "a" or "an" used to describe an element, ingredient, part or step is not intended to exclude other elements, ingredients, parts or steps.

The above-mentioned various embodiments in this specification are described in a progressive manner, and the same and similar parts between the various embodiments may be referred to each other, and each embodiment focuses on the differences from other embodiments.

The above descriptions are only a few embodiments of the present invention. Although the embodiments disclosed in the present invention are as above, the above-described content is only an embodiment adopted to facilitate the understanding of the present invention, and is not intended to limit the present invention. Any person skilled in the art to which the present invention pertains, without departing from the spirit and scope disclosed by the present invention, can make any modifications and changes in the form and details of the embodiments, but the scope of patent protection of the present invention, The scope as defined by the appended claims shall still prevail.

Claims (18)

1. A pump head structure, comprising: a transmission head, a diaphragm and a valve seat which are arranged in sequence along the direction of the output shaft of the motor,

the diaphragm is provided with a first surface matched with the transmission head and a second surface matched with the valve seat;

the second surface is provided with a plurality of wading portions which can contact with fluid, a pressurizing cavity is formed between each wading portion and the valve seat, and the area ratio of the wading portions to the diaphragm is as follows: 50 to 70 percent.

2. A pump head construction as claimed in claim 1, wherein the diaphragm includes a seal not less than a predetermined size disposed between an edge of the diaphragm and the water-engaging portion to cooperate with the valve seat.

3. A pump head construction according to claim 2, wherein the second surface of the diaphragm is provided with a rib on the seal between two adjacent said water-engaging portions.

4. A pump head construction as claimed in claim 1, wherein the edge of the water-engaging portion is an arcuate transition.

5. A pump head structure as claimed in claim 4, wherein the shape defined by the rim of the water-engaging portion comprises any one of: oval, irregular round-like.

6. A pump head structure according to claim 1, wherein the number of wobblers corresponding to the number of the water-receiving portions is provided on the drive head, and an area ratio of the wobblers to the water-receiving portions is 70% to 90%, and wherein an area ratio of the wobblers to the water-receiving portions is a projected area ratio of the wobblers and the water-receiving portions on the same reference plane along the direction of the motor output shaft.

7. A pump head construction according to claim 6, wherein the balance wheel is oval in cross-section.

8. A pump head structure as claimed in claim 1, wherein the ratio of the minimum distance from the outermost chamber wall of the pumping chamber to the pump head periphery to the diameter of the pump head is in the range 4% to 6%.

9. A pump head structure as claimed in claim 1, wherein the ratio of the minimum distance between the walls of two adjacent pumping chambers to the diameter of the pump head is in the range 8% to 10%.

10. A pump head structure as claimed in claim 1, wherein the number of said pumping chambers is 3, and 3 of said pumping chambers are evenly distributed around said motor output shaft.

11. A pump head construction as claimed in claim 1, wherein the cross-sectional shape of the pumping chamber is elliptical or irregular round-like.

12. A pump head structure as claimed in claim 1, wherein the first surface of the diaphragm abuts against a pump cover, the drive head is provided with a number of wobblers matching the number of the paddle portions, and the pump cover is provided with an opening through which the wobblers are inserted.

13. A pump head structure as claimed in claim 12, wherein the aperture is in clearance fit with the balance, the clearance being between 0.8mm and 1.5 mm.

14. A pump head structure as claimed in claim 12, wherein the wobbler occupies an area that is 42% to 60% of the cross-sectional area of the entire pump head.

15. A pump head construction as claimed in claim 12, wherein the aperture is an elliptical aperture.

16. A pump head structure as claimed in claim 1, wherein the area ratio of the water-engaging portion to the diaphragm is: a projected area ratio of the water-involved section to the diaphragm on the same reference plane along the motor output shaft direction.

17. A diaphragm pump, comprising: a pump head structure as claimed in any one of claims 1 to 16, and a motor for providing a driving force to the drive head.

18. The diaphragm pump of claim 17 wherein said motor rotates at a speed of: the output torque is between 0.4N.M and 0.8N.M at 1200RPM to 1800RPM, and the flow rate of the diaphragm pump is as follows: 4LPM to 8 LPM.

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