Diaphragm pump driven by axial integrated motor

Abstract

The invention discloses a diaphragm pump driven by an axial integrated motor, and relates to the technical field of diaphragm pumps, the diaphragm pump comprises a pump body assembly and a driving assembly, and the pump body assembly is provided with a fluid inlet and a fluid outlet which are communicated; the driving assembly comprises a cam, a sliding part and a diaphragm, the diaphragm is arranged in the pump body assembly and divides the interior of the pump body assembly into a containing cavity and a fluid channel, the fluid channel communicates with the fluid inlet and the fluid outlet, the sliding part is arranged in the containing cavity in a sliding mode and connected to the diaphragm, and the cam is rotationally arranged in the containing cavity and provided with a plurality of force application protrusions arranged along the circumferential side of the cam. When the cam rotates, the multiple force application protrusions can be driven to drive the sliding piece to slide in a reciprocating mode one by one, the sliding piece can drive the diaphragm to swing in a reciprocating mode when sliding so as to drive the fluid channel to be continuously switched between the positive pressure and the negative pressure, fluid is driven to sequentially pass through the inlet and the fluid channel and then be discharged out of the outlet, and the purpose of fluid conveying is achieved. When the cam rotates by one circle, the diaphragm can be driven to move for multiple times, and the working efficiency of the diaphragm pump is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of diaphragm pumps, and in particular to a diaphragm pump driven by an axially integrated motor. Background Art

[0002] The diaphragm pump, also known as the control pump, is a new type of conveying machinery and a new type of pump. It can use air, electric devices, liquid media, etc. as power to intake and pump liquids. Unlike other conventional pumps, traditional diaphragm pumps are usually composed of key components such as motors, drive shafts, eccentric wheels, connecting rods and diaphragms. The motor drives the drive shaft and eccentric wheel and other linkage structures to drive the internal diaphragm to swing back and forth to change the volume of the cavity and realize the suction and discharge of the medium.

[0003] However, existing diaphragm pumps still have shortcomings. For example, the movement of the diaphragm is caused by the rotation of the eccentric wheel driven by the motor. The eccentric wheel rotates one full circle to drive the diaphragm to move once, resulting in low working efficiency of the diaphragm pump. Summary of the Invention

[0004] The purpose of the present invention is to overcome the above-mentioned technical deficiencies and propose a diaphragm pump driven by an axially integrated motor to solve the technical problem in the prior art that the eccentric wheel of the diaphragm pump needs to rotate a full circle to drive the diaphragm to move once, resulting in low working efficiency of the diaphragm pump.

[0005] In order to achieve the above technical objectives, the present invention adopts the following technical solutions: The present invention provides an axially integrated motor-driven diaphragm pump, comprising: a pump assembly having a fluid inlet and a fluid outlet in communication; and The drive assembly includes a cam, a sliding member and a diaphragm. The diaphragm is arranged inside the pump body assembly and divides the inside of the pump body assembly into a accommodating chamber and a fluid channel. The fluid channel connects the fluid inlet and the fluid outlet. The sliding member is slidably arranged in the accommodating chamber and is connected to the diaphragm. When sliding, the sliding member can drive the diaphragm to swing back and forth to drive the fluid channel to continuously switch between positive pressure and negative pressure. The cam is rotatably arranged in the accommodating chamber. The cam has a plurality of force-applying protrusions arranged along its circumference. When rotating, the cam can drive the plurality of force-applying protrusions to drive the sliding member to slide back and forth one by one.

[0006] In some embodiments, a retreat groove is formed between adjacent force-applying protrusions, and when the sliding member moves to the retreat groove, the diaphragm drives the fluid channel to form a negative pressure.

[0007] In some embodiments, the sliding member has a guide arc surface at one end facing the cam, and the guide arc surface can drive the sliding member to slide when pressed by the force-applying protrusion.

[0008] In some embodiments, the drive assembly further includes a return spring, which is connected to the sliding member and can accumulate or release elastic force when the sliding member slides back and forth.

[0009] In some embodiments, the driving assembly further includes a permanent magnet motor, which is disposed in the accommodating cavity and connected to the cam to drive the cam to rotate.

[0010] In some embodiments, the permanent magnet motor includes a first stator group, a second stator group, and a rotor. The rotor is located between the first stator group and the second stator group, and the rotor is coaxially connected to the cam.

[0011] In some embodiments, the pump body assembly further includes two serpentine cooling pipes, which are cross-distributed in the gap between the first stator assembly and the rotor and fit closely to the rotor.

[0012] In some embodiments, the pump body assembly also includes a first sealing ball and a second sealing ball, and the first sealing ball and the second sealing ball are respectively arranged at the inlet and outlet of the fluid channel. When the fluid channel is in a negative pressure state, the first sealing ball opens the inlet of the fluid channel, and the second sealing ball seals the outlet of the fluid channel; when the fluid channel is in a positive pressure state, the first sealing ball seals the inlet of the fluid channel, and the second sealing ball opens the outlet of the fluid channel.

[0013] In some embodiments, the fluid channel includes a first channel and a second channel, the first sealing ball and the second sealing ball are respectively arranged at the inlet and outlet of the first channel, the number of the diaphragms and the sliding parts are two, the two diaphragms and the two sliding parts are respectively located on opposite sides of the cam, and the two diaphragms can respectively drive the first channel and the second channel to switch between positive pressure and negative pressure when moving.

[0014] In some embodiments, the pump body assembly further includes a third sealing ball and a fourth sealing ball, wherein the third sealing ball and the fourth sealing ball are respectively disposed at the inlet and the outlet of the second channel.

[0015] Compared to the prior art, the diaphragm pump provided by the present invention has a cam that, when rotated, drives the sliding member to slide back and forth, thereby driving the reciprocating motion of the diaphragm. During this reciprocating motion, the diaphragm can drive the fluid channel to switch between positive and negative pressures, driving the fluid through the inlet and the fluid channel in sequence, and then out of the outlet, achieving the purpose of fluid transportation. The cam of the present invention has multiple force-applying protrusions arranged along its circumference. When the cam rotates, it can drive the multiple force-applying protrusions to drive the sliding member to slide back and forth one by one; therefore, the cam can drive the diaphragm to move multiple times during one rotation, thereby improving the operating efficiency of the diaphragm pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 Schematic diagram of the structure of a diaphragm pump provided by an embodiment of the present invention; Figure 2 is a schematic diagram of the interior of a diaphragm pump provided by an embodiment of the present invention; Figure 3 is a structural schematic diagram of a permanent magnet motor provided by an embodiment of the present invention; Figure 4 It is a structural schematic diagram of the connection between a permanent magnet motor and a serpentine cooling pipe provided by an embodiment of the present invention. DETAILED DESCRIPTION

[0017] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0018] In order to solve the technical problem in the prior art that the eccentric wheel of the diaphragm pump needs to rotate a full circle to drive the diaphragm to move once, resulting in low working efficiency of the diaphragm pump, the present invention provides a diaphragm pump driven by an axially integrated motor, which can achieve that the cam rotates one circle to drive the diaphragm to move multiple times, thereby improving the operating efficiency of the diaphragm pump.

[0019] See also Figure 1 and Figure 2 , Figure 1This is a structural schematic diagram of a diaphragm pump in an embodiment of the present invention. The diaphragm pump 100 includes a pump body assembly 1 and a drive assembly 2. The pump body assembly 1 has a connected fluid inlet 11 and a fluid outlet 12; the drive assembly 2 includes a cam 21, a sliding member 22 and a diaphragm 23. The diaphragm 23 is arranged inside the pump body assembly 1 and divides the inside of the pump body assembly 1 into a accommodating chamber 13 and a fluid channel 14. The fluid channel 14 connects the fluid inlet 11 and the fluid outlet 12. The sliding member 22 is slidably arranged in the accommodating chamber 13 and connected to the diaphragm 23. The cam 21 is rotatably arranged in the accommodating chamber 13 and can drive the sliding member 22 to slide back and forth when rotating. The sliding member 22 can drive the diaphragm 23 to swing back and forth when sliding, so as to drive the fluid channel 14 to continuously switch between positive pressure and negative pressure, thereby realizing the suction and discharge of fluid and achieving the purpose of fluid transportation.

[0020] In this embodiment, the drive assembly 2 is integrated into the interior of the pump body assembly 1, and the movement of the diaphragm 23 is achieved by the cam 21 pressing the sliding member 22 to slide, which has a simple structure; the transmission chain formed by the cam 21 and the sliding member 22 is short, occupies a small space, reduces energy loss, and improves the operating efficiency of the diaphragm pump 100.

[0021] The fluid inlet 11 and fluid outlet 12 of the pump assembly 1 are both provided with flanges 19, which are used to screw the pump assembly 1. The bottom of the pump assembly 1 has a mounting bracket 20, which is used to pass screws through to secure the bottom of the pump assembly 1.

[0022] In one embodiment, see Figure 2 The cam 21 has multiple force-applying projections 211 around its circumference. As the cam 21 rotates, the force-applying projections 211 press against the sliding member 22, forcing a positive pressure into the fluid channel 14. Relief grooves 212 are formed between adjacent force-applying projections 211. When the sliding member 22 moves into the relief grooves 212, the diaphragm 23 deforms away from the fluid channel 14, creating a negative pressure therein, forcing fluid from the inlet 11 into the fluid channel 14. Specifically, as the cam 21 rotates clockwise or counterclockwise, the multiple force-applying projections 211 sequentially contact the sliding member 22, pushing it in a certain direction. This reduces the volume of the fluid channel 14, creates a positive pressure, and forces the fluid out of the outlet 12. When the sliding member 22 reaches the relief grooves 212, the volume of the fluid channel 14 increases, creating a negative pressure and drawing fluid in. The cam 21 can rotate at 300 to 1000 revolutions per minute to accommodate various fluid delivery requirements. There are five force-applying protrusions 211 evenly distributed around the cam 21 to ensure smooth reciprocating movement of the slider 22. The width of the relief groove 212 is slightly larger than the diameter of the slider 22 to ensure that the slider 22 can slide accurately into the relief groove 212 and form a negative pressure in the fluid channel 14.

[0023] In addition, the thickness of the cam 21 is greater than the width of the sliding member 22, and the sliding member 22 is located within the thickness direction range of the cam 21, so that when the cam 21 rotates, the sliding member 22 can fully contact the force protrusion 211 to ensure the smooth reciprocating sliding of the sliding member 22. The sliding member 22 drives the diaphragm 23 to swing back and forth, and can stably transport the fluid.

[0024] In one embodiment, see Figure 2 The end of the sliding member 22 facing the cam 21 has a guide arc surface 221, and the guide arc surface 221 can drive the sliding member 22 to slide when it is pressed by the force-applying protrusion 211. The design of the guide arc surface 221 enables the sliding member 22 to slide more smoothly when it is pressed by the force-applying protrusion 211, reduces the friction between the sliding member 22 and the cam 21, and improves the transmission efficiency. The curvature radius of the guide arc surface 221 matches the end curvature radius of the force-applying protrusion 211 to ensure close contact and effective transmission between the two. The material of the sliding member 22 can be a high-strength aluminum alloy to ensure its structural strength and wear resistance during long-term reciprocating sliding. The surface of the sliding member 22 is hardened to further improve its wear resistance and fatigue resistance, thereby extending its service life.

[0025] In one embodiment, see Figure 2 The drive assembly 2 also includes a return spring 24, which is connected to the slider 22 and is capable of storing or releasing elastic force as the slider 22 reciprocates. When the slider 22 is pushed and slid by the cam 21, the return spring 24 is compressed, storing elastic potential energy. When the slider 22 slides to the position of the retreat groove 212, the return spring 24 releases its elastic potential energy, assisting the diaphragm 23 in rebounding, quickly forming a negative pressure in the fluid channel 14 and improving fluid suction efficiency. The spring constant of the return spring 24 can be designed based on the size of the diaphragm 23 and the required negative pressure to ensure that the return spring 24 can provide sufficient elastic force to assist the diaphragm 23 in rebounding. The free length of the return spring 24 can be set to five to ten centimeters to ensure that the return spring 24 has sufficient elastic travel. The two ends of the return spring 24 are connected to the slider 22 and the inner wall of the accommodating chamber 13 respectively by snap fasteners or threads, ensuring a secure connection and preventing the return spring 24 from loosening during high-speed reciprocating motion.

[0026] In one embodiment, see Figure 2The drive assembly 2 also includes a permanent magnet motor 25, which is arranged in the accommodating chamber 13 and connected to the cam 21 to drive the cam 21 to rotate. The permanent magnet motor 25 has the advantages of high efficiency, energy saving, small size, light weight, etc., and can provide stable rotational power for the cam 21. The rated power of the permanent magnet motor 25 is 0.5 to 2 kilowatts, which is selected according to the actual fluid conveying requirements. The speed range of the permanent magnet motor 25 can be set to 300 to 1500 rpm, which matches the speed requirement of the cam 21. The permanent magnet motor 25 can be coaxially connected to the cam 21 through a coupling to ensure the efficiency and stability of power transmission. The coupling adopts an elastic coupling, which can effectively buffer the torque fluctuations during the operation of the motor and protect components such as the cam 21 and the sliding part 22 from impact damage.

[0027] In one embodiment, see Figure 4 The permanent magnet motor 25 includes a first stator group 251, a second stator group 252 and a rotor 253. The rotor 253 is located between the first stator group 251 and the second stator group 252, and the rotor 253 is coaxially connected to the cam 21. The first stator group 251 and the second stator group 252 are respectively fixed on the inner walls on both sides of the accommodating cavity 13 to form a stable support for the rotor 253. The rotor 253 can be made of high-performance neodymium iron boron permanent magnet material, which has strong magnetic properties and can generate a strong magnetic field to improve the operating efficiency of the motor. The air gap between the rotor 253 and the first stator group 251 and the second stator group 252 can be set to 0.5 to 2 mm. Precisely controlling the size of the air gap can effectively improve the performance and efficiency of the motor and reduce leakage magnetic field and eddy current loss. The surface of the rotor 253 can be treated with a wear-resistant coating to enhance its wear resistance and oxidation resistance in long-term operation and extend its service life.

[0028] In one embodiment, see Figure 3 and Figure 4The pump body assembly 1 also includes two serpentine cooling pipes 15, which are cross-distributed in the gap between the first stator group 251 and the rotor 253 and fit the rotor 253. In this embodiment, the serpentine cooling pipes 15 are filled with coolant, which can effectively take away the heat generated during the operation of the permanent magnet motor 25 and ensure that the motor operates stably within an appropriate temperature range. The coolant can be a water-ethylene glycol mixture, which has good cooling and antifreeze properties. The diameter of the serpentine cooling pipe 15 can be set to three to eight millimeters, with a wall thickness of 0.5 to 1.5 millimeters, and is made of corrosion-resistant and high-pressure resistant materials, such as stainless steel or special engineering plastics. The layout design of the serpentine cooling pipe 15 is cross-type to maximize the contact area with the rotor 253 and improve the heat dissipation efficiency. The inlet and outlet of the cooling pipe 15 are respectively located on both sides of the pump body assembly 1, which is convenient for connection with other cooling systems to form a circulating cooling loop. The flow rate of the coolant can be controlled at 1 to 3 m / s to ensure a good cooling effect while avoiding excessive pressure loss due to excessive flow rate.

[0029] In one embodiment, see Figure 2 The pump assembly 1 also includes a first sealing ball 16 and a second sealing ball 17, which are respectively positioned at the inlet and outlet of the fluid channel 14. When the fluid channel 14 is under negative pressure, the negative pressure drives the first sealing ball 16 upward, opening the inlet of the fluid channel 14 and allowing fluid to enter. Simultaneously, the negative pressure drives the second sealing ball 17 downward, sealing the outlet of the fluid channel 14. When the fluid channel 14 is under positive pressure, the first sealing ball 16 seals the inlet of the fluid channel 14, while the second sealing ball 17, under pressure from the fluid channel, moves upward to open the outlet of the fluid channel 14. In this embodiment, the diameters of the first and second sealing balls 16, 17 are slightly larger than the inner diameters of the inlet and outlet of the fluid channel 14 to ensure a good sealing effect. The sealing ball surfaces are finely polished to a mirror-like finish to reduce friction with the inner wall of the fluid channel 14, thereby improving sealing reliability and service life. The inner walls of the inlet and outlet of fluid channel 14 are provided with guiding tapered surfaces to accurately guide the sealing balls to open and close the channel, preventing them from deflecting or becoming stuck under the impact of high-speed fluid. In this embodiment, the alternating motion of first and second sealing balls 16, 17 under positive and negative pressures allows fluid to be drawn into and discharged from the outlet of fluid channel 14, achieving fluid transfer.

[0030] In one embodiment, see Figure 2 In one embodiment, see Figure 2The fluid channel 14 includes a first channel 141 and a second channel 142. The first channel 141 is generally linear, while the second channel 142 is generally C-shaped. The inlets of the first channel 141 and the second channel 142 are both located near the fluid inlet 11, and the inlets of the first channel 141 and the second channel 142 are both located near the fluid outlet 12. A first sealing ball 16 and a second sealing ball 17 are located at the inlet and outlet of the first channel 141, respectively. There are two diaphragms 23 and two sliding members 22, each defined as a first diaphragm 231 and a second diaphragm 232, and a first sliding member 221 and a second sliding member 222, respectively. The two diaphragms and the two sliding members are located on opposite sides of the cam 21. The first diaphragm 231, when in motion, can switch the first channel 141 between positive and negative pressures. The second diaphragm 232, when in motion, can switch the second channel 142 between positive and negative pressures. A third sealing ball 18 and a fourth sealing ball 19 are located at the inlet and outlet of the second channel 142, respectively. In this embodiment, the force-applying protrusions 211 and the retreat grooves 212 on the cam 21 are arranged in an alternating manner. When the force-applying protrusions 211 of the cam 21 press against the first sliding member 221, the second sliding member 222 is exactly located in the retreat groove 212 on the other side of the cam 21; when the force-applying protrusions 211 of the cam 21 press against the second sliding member 222, the first sliding member 221 is exactly located in the retreat groove 212 on the other side of the cam 21. In other words, only one of the first diaphragm 231 and the second diaphragm 232 moves at a time. The two diaphragms move alternately without affecting the air pressure in the corresponding channels, thereby continuously and alternately drawing fluid into the corresponding channels and continuously and alternately discharging the fluid in the corresponding channels from the corresponding outlets. This dual-channel design enables the diaphragm pump to deliver more fluid per unit time, thereby improving fluid delivery efficiency. The two diaphragms 23 and the two sliding members 22 are symmetrically arranged on both sides of the cam 21. When the cam 21 rotates, it can drive the two sliding members 22 to move at the same time, so as to simultaneously drive the two diaphragms 23 to move through the two sliding members 22, which not only improves the fluid delivery efficiency, but also ensures the force balance during the rotation of the cam 21, and reduces vibration and noise.

[0031] In order to better understand the present invention, the following Figures 1 to 4 The technical solution of the present invention is described in detail: The diaphragm pump 100 provided by the present invention has a cam 21 that, when rotated, can drive the sliding member 22 to slide back and forth, thereby driving the diaphragm 23 to reciprocate. During the reciprocating motion, the diaphragm 23 can drive the fluid channel 14 to switch between positive and negative pressures, thereby driving the fluid to pass through the inlet and the fluid channel in sequence and then be discharged from the outlet, thereby achieving the purpose of fluid transportation. The cam 21 of the present invention has multiple force-applying protrusions 211 arranged along its circumference. When the cam 21 rotates, it can drive the multiple force-applying protrusions 211 to drive the sliding member 221 to slide back and forth one by one; therefore, the cam 21 can drive the diaphragm to move multiple times during one rotation, thereby improving the operating efficiency of the diaphragm pump.

[0032] The specific embodiments of the present invention described above do not limit the scope of protection of the present invention. Any other corresponding changes and modifications made based on the technical concept of the present invention should be included in the scope of protection of the claims of the present invention.

Claims

1. A diaphragm pump driven by an axially integrated motor, characterized in that: include: a pump body assembly having a fluid inlet and a fluid outlet in communication; and The drive assembly includes a cam, a sliding member and a diaphragm. The diaphragm is arranged inside the pump body assembly and divides the inside of the pump body assembly into a accommodating chamber and a fluid channel. The fluid channel connects the fluid inlet and the fluid outlet. The sliding member is slidably arranged in the accommodating chamber and is connected to the diaphragm. When sliding, the sliding member can drive the diaphragm to swing back and forth to drive the fluid channel to continuously switch between positive pressure and negative pressure. The cam is rotatably arranged in the accommodating chamber. The cam has a plurality of force-applying protrusions arranged along its circumference. When rotating, the cam can drive the plurality of force-applying protrusions to drive the sliding member to slide back and forth one by one.

2. The axially integrated motor-driven diaphragm pump according to claim 1, characterized in that: An escape groove is formed between adjacent force-applying protrusions. When the sliding member moves to the escape groove, the diaphragm drives the fluid channel to form a negative pressure.

3. The axially integrated motor-driven diaphragm pump according to claim 2, characterized in that: One end of the sliding member facing the cam has a guide arc surface, and the guide arc surface can drive the sliding member to slide when pressed by the force-applying protrusion.

4. The axially integrated motor-driven diaphragm pump according to claim 1, characterized in that: The driving assembly further includes a return spring, which is connected to the sliding member and can accumulate or release elastic force when the sliding member slides back and forth.

5. The axially integrated motor-driven diaphragm pump according to claim 1, characterized in that: The driving assembly further includes a permanent magnet motor, which is disposed in the accommodating cavity and connected to the cam to drive the cam to rotate.

6. The axially integrated motor-driven diaphragm pump according to claim 5, characterized in that: The permanent magnet motor includes a first stator group, a second stator group and a rotor. The rotor is located between the first stator group and the second stator group, and the rotor is coaxially connected to the cam.

7. The axially integrated motor-driven diaphragm pump according to claim 6, characterized in that: The pump body assembly further includes two serpentine cooling pipes, which are cross-distributed in the gap between the first stator assembly and the rotor and fit closely to the rotor.

8. The axially integrated motor-driven diaphragm pump according to claim 1, characterized in that: The pump assembly further comprises a first sealing ball and a second sealing ball, wherein the first sealing ball and the second sealing ball are respectively arranged at the inlet and outlet of the fluid channel. When the fluid channel is in a negative pressure state, the first sealing ball opens the inlet of the fluid channel and the second sealing ball seals the outlet of the fluid channel. When the fluid channel is in a positive pressure state, the first sealing ball seals the inlet of the fluid channel, and the second sealing ball opens the outlet of the fluid channel.

9. The axially integrated motor-driven diaphragm pump according to claim 8, characterized in that: The fluid channel includes a first channel and a second channel, the first sealing ball and the second sealing ball are respectively arranged at the inlet and outlet of the first channel, the number of the diaphragms and the number of the sliding parts are both two, the two diaphragms and the two sliding parts are respectively located on opposite sides of the cam, and the two diaphragms can respectively drive the first channel and the second channel to switch between positive pressure and negative pressure when moving.

10. The axially integrated motor-driven diaphragm pump according to claim 9, characterized in that: The pump body assembly further includes a third sealing ball and a fourth sealing ball, and the third sealing ball and the fourth sealing ball are respectively arranged at the inlet and the outlet of the second channel.

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