Pulseless helical tooth type pump

Abstract

The utility model relates to the technical field of sausage filling material conveying, and provides a pulseless helical tooth type pump which comprises a pump body, the pump body is provided with a pump cavity, and the pump cavity is provided with an inlet and an outlet. The first bevel gear and the second bevel gear are both rotationally arranged in the pump cavity and meshed with each other, a material pumping gap is formed between the first bevel gear and the second bevel gear, the inlet faces the material pumping gap, the material pumping gap faces the outlet, the first bevel gear and the second bevel gear are each provided with a plurality of helical teeth arranged circumferentially, the upper ends of the helical teeth are tooth crests, and the lower ends of the helical teeth are tooth crests. The helical teeth are configured in the mode that before the meshed tooth roots of the first helical gear and the second helical gear exit from meshing, the first helical gear and the second helical gear still have at least one meshed tooth crest. According to the technical scheme, the gear pump for enema in the related technology has pressure pulsation, certain pressure pulsation can be generated in the conveying process, and certain influences are generated on the stability and uniformity of enema.

Description

Technical Field

[0001] The utility model relates to the technical field of enema material transportation, and specifically, to a non-pulsating helical gear pump. Background Art

[0002] The gear pump for enema is a pump specifically designed for transporting materials during the enema process. It usually consists of two meshing gears. When the gears rotate, a local vacuum is formed on the suction side of the pump, thereby sucking the enema material into the pump cavity (101). As the gears continue to rotate, the material is transported to the discharge side of the pump and discharged with a certain pressure and flow rate, realizing the stable and quantitative transportation of the enema material. This kind of gear pump has the advantages of compact structure and good sealing performance, and can meet the requirements of material transportation in enema production. However, the gear pump for enema in the prior art usually has some disadvantages. For example, there is pressure pulsation. During the transportation process, certain pressure pulsation may occur, which may have a certain impact on the stability and uniformity of the enema. At the same time, it is not suitable for high-viscosity materials. For some high-viscosity enema materials, the transportation effect of the gear pump may not be ideal. Summary of the Utility Model

[0003] The utility model provides a non-pulsating helical gear pump, which solves the technical problem that the gear pump for enema in the related technology has pressure pulsation during the transportation process, which will have a certain impact on the stability and uniformity of the enema.

[0004] The technical solution of the utility model is as follows:

[0005] The non-pulsating helical gear pump includes:

[0006] A pump body, the pump body has a pump cavity, and the pump cavity has an inlet and an outlet;

[0007] A first helical gear and a second helical gear, the first helical gear and the second helical gear are both rotatably arranged in the pump cavity and mesh with each other, and there is a pump material gap between them. The inlet faces the pump material gap, and the pump material gap faces the outlet. Wherein the first helical gear and the second helical gear both have a number of helical teeth arranged in a circumferential manner. The upper end of the helical tooth is the tooth tip, and the lower end is the tooth root. The helical teeth are configured such that before the tooth roots of the first helical gear and the second helical gear that mesh with each other withdraw from meshing, there is still at least one tooth tip of the first helical gear and the second helical gear that mesh with each other.

[0008] In this embodiment, in order to solve the problems that the gear pump for enema has pressure pulsation, which affects the stability and uniformity of enema, and has poor conveying effect on high-viscosity materials, a pulsation-free helical gear pump is designed, including a pump body, the pump body has a pump chamber, and the pump chamber has an inlet and an outlet. The design principle is to provide space and channels for the inlet, outlet and conveying of materials. The technical effect is to ensure that the materials can smoothly enter and discharge from the pump body, realizing effective conveying.

[0009] The first helical gear and the second helical gear are both rotatably arranged in the pump chamber and mesh with each other, there is a pump material gap between them, the inlet faces the pump material gap, and the pump material gap faces the outlet. The design principle is to realize the pushing of materials through the meshing rotation of the two helical gears. The technical effect is to be able to stably push the materials from the inlet to the outlet, realizing the conveying of materials.

[0010] As a further technical solution, the helical teeth are configured such that before the tooth roots of the first helical gear and the second helical gear disengaged from meshing, there are still 1 - 4 tooth tips of the first helical gear and the second helical gear meshing with each other.

[0011] As a further technical solution, the module of the first helical gear and the second helical gear is between 1.5 - 5 mm, and the modules of the first helical gear and the second helical gear are the same.

[0012] As a further technical solution, the helix angle β of the first helical gear and the second helical gear is 15° - 30°.

[0013] As a further technical solution, the ratio of the tooth width to the pitch diameter of the first helical gear and the second helical gear is between 0.2 - 0.4.

[0014] As a further technical solution, the normal pressure angle of the first helical gear and the second helical gear is 22° - 25°.

[0015] As a further technical solution, the addendum coefficient of the first helical gear and the second helical gear is 1.1 - 1.3. Appropriately increasing the addendum coefficient can increase the addendum thickness and improve the anti-wear ability of the addendum, thereby extending the service life of the gear.

[0016] As a further technical solution, the clearance coefficient of the first helical gear and the second helical gear is 0.3 - 0.4. A larger clearance coefficient can provide more storage space for lubricating oil, help improve the lubrication conditions of the tooth surface, and reduce wear and heat generation.

[0017] As a further technical solution, the ratio of the pitch diameter of the first helical gear to the pitch diameter of the second helical gear is between 1.2 and 1.5. By limiting the ratio of the pitch diameters of the two gears, the flow characteristics of the pump are optimized and the working efficiency of the pump is improved.

[0018] As a further technical solution, the tooth roots of the first helical gear and the second helical gear are configured such that the transition curve adopts an optimized involute-arc transition.

[0019] The working principle and beneficial effects of the present utility model are as follows:

[0020] In the present utility model, a pulsation-free helical pump is designed, which includes a pump body having a pump chamber with an inlet and an outlet. The design principle is to provide space and channels for the inlet and outlet of the material and its transportation. The technical effect is to ensure that the material can smoothly enter and exit the pump body, achieving effective transportation. The first helical gear and the second helical gear are both rotatably arranged in the pump chamber and mesh with each other, with a pump material gap therebetween. The inlet faces the pump material gap, and the pump material gap faces the outlet. The design principle is to push the material through the meshing rotation of the two helical gears. The technical effect is that the material can be stably pushed from the inlet to the outlet, realizing the transportation of the material. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The following will further illustrate the above characteristics, technical features, advantages and their implementation manners of the present utility model in a clear and understandable manner in combination with the drawings of the preferred embodiments.

[0022] Figure 1 is a schematic structural diagram of the present utility model;

[0023] Figure 2 is a schematic structural diagram of the first helical gear and the second helical gear in the present utility model;

[0024] In the figure: pump body - 1, pump chamber - 101, inlet - 102, outlet - 103, first helical gear - 2, second helical gear - 3, pump material gap - 201, helical teeth - 202, tooth tip - 203, tooth root - 204. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0025] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the specific embodiments of the present utility model will be described below with reference to the drawings. Obviously, the drawings in the following description are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings and other embodiments can be obtained.

[0026] To make the drawings concise, only the parts related to the utility model are schematically shown in each drawing, and they do not represent the actual structure of the product. Additionally, to make the drawings concise and easy to understand, for components with the same structure or function in some drawings, only one of them is schematically shown, or only one of them is labeled. In this article, "one" not only means "only this one", but also can mean "more than one" situation, and "several" includes "two" and "more than two".

[0027] In this article, it should be noted that unless otherwise clearly specified and limited, the terms "install", "connect", and "join" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in this utility model can be understood according to specific situations.

[0028] In addition, in the description of this application, the terms "first", "second", etc. are only used for distinguishing descriptions and cannot be understood as indicating or implying relative importance.

[0029] Refer to Figure 1 - Figure 2 , this embodiment proposes a non-pulsating helical gear pump, which includes a pump body 1. The pump body 1 has a pump chamber 101. The pump chamber 101 has an inlet 102 and an outlet 103. The first helical gear 2 and the second helical gear 3 are both rotatably arranged in the pump chamber 101 and mesh with each other, and there is a pump material gap 201 between them. The inlet 102 faces the pump material gap 201, and the pump material gap 201 faces the outlet 103. Wherein, both the first helical gear 2 and the second helical gear 3 have several helical teeth 202 arranged in a circumferential manner. The upper end of the helical tooth 202 is the tooth tip 203, and the lower end is the tooth root 204. The helical teeth 202 are configured such that before the tooth roots 204 of the first helical gear 2 and the second helical gear 3 that mesh with each other withdraw from the engagement, there is still at least one tooth tip 203 of the first helical gear 2 and the second helical gear 3 that mesh with each other.

[0030] In this embodiment, in order to solve the problems that the gear pump for enema has pressure pulsation, which affects the stability and uniformity of enema, and has poor conveying effect on high-viscosity materials, a non-pulsating helical gear pump is designed, which includes a pump body 1. The pump body 1 has a pump chamber 101. The pump chamber 101 has an inlet 102 and an outlet 103. The design principle is to provide space and channels for the inlet, outlet and conveying of materials. The technical effect is to ensure that the materials can smoothly enter and discharge from the pump body and achieve effective conveying.

[0031] The first helical gear 2 and the second helical gear 3 are both rotatably arranged in the pump chamber 101 and mesh with each other, with a pump material gap 201 therebetween. The inlet 102 faces the pump material gap 201, and the pump material gap 201 faces the outlet 103. The design principle is to realize the pushing of materials through the meshing rotation of the two helical gears. The technical effect is that the materials can be stably pushed from the inlet to the outlet to realize the conveying of materials.

[0032] Among them, both the first helical gear 2 and the second helical gear 3 have a number of helical teeth 202 arranged circumferentially. The upper end of the helical tooth 202 is the tooth tip 203, and the lower end is the tooth root 204. The helical teeth 202 are configured such that before the tooth roots 204 of the first helical gear 2 and the second helical gear 3 that mesh with each other disengage, there is still at least one tooth tip 203 of the first helical gear 2 and the second helical gear 3 that mesh with each other. The design principle is that through this special helical tooth meshing structure, it is ensured that there are enough meshing points at any time to realize continuous and stable material pushing. The technical effect is that the pressure pulsation is effectively eliminated, the material conveying is more stable and uniform, and at the same time, the conveying capacity for high-viscosity materials can be improved. Through the synergistic effect of the pump body 1, the first helical gear 2, the second helical gear 3 and the specially designed helical tooth 202 structure, the stable and pulsation-free conveying of the enema material is realized. This non-pulsating helical gear pump successfully solves the pressure pulsation problem of the existing gear pump for enema, improves the stability and uniformity of enema. At the same time, the conveying effect for high-viscosity materials is significantly improved, which can meet the high-quality requirements for the conveying of different materials in enema production, and improves the production efficiency and product quality.

[0033] Furthermore, the helical teeth 202 are configured such that before the tooth roots 204 of the first helical gear 2 and the second helical gear 3 that mesh with each other disengage, there are still 1 - 4 tooth tips 203 of the first helical gear 2 and the second helical gear 3 that mesh with each other.

[0034] In this embodiment, when the helical teeth are configured such that before the tooth roots of the first helical gear and the second helical gear that mesh with each other disengage, there are 1 - 4 tooth tips that mesh with each other, its technical effect lies in that the smoothness of material pushing during the gear meshing process can be more precisely controlled. A smaller number of meshing tooth tips, such as 1, can reduce friction and energy loss to a certain extent, while a larger number of meshing tooth tips, such as 4, can provide stronger stability and load-bearing capacity. Through this adjustable design, according to different material characteristics and working conditions, the working performance of the pump can be optimized, further reducing the pressure pulsation, improving the uniformity and stability of material conveying, and at the same time, it can also meet the wider enema production requirements.

[0035] Furthermore, the module of the first helical gear 2 and the second helical gear 3 is between 1.5 - 5 mm, and the modules of the first helical gear 2 and the second helical gear 3 are the same.

[0036] In this embodiment, when the module of the first helical gear 2 and the second helical gear 3 is between 1.5 - 5 mm and the modules are the same, the technical effect is that it can ensure the smoothness and consistency of the gears during transmission. The appropriate module range can provide sufficient strength and load-bearing capacity to meet the conveying pressure and flow requirements of the enema material. The same module ensures the mating accuracy during the meshing of the two gears and the stability of the transmission ratio, reducing the transmission error and energy loss caused by the module difference. This helps to further improve the working efficiency and stability of the pump, reduce noise and vibration, extend the service life of the gears, and thus enhance the performance and reliability of the entire pulsation-free helical gear pump.

[0037] Furthermore, the helix angle β of the first helical gear 2 and the second helical gear 3 is 15° - 30°.

[0038] In this embodiment, when the helix angle β of the first helical gear 2 and the second helical gear 3 is in the range of 15° - 30°, the technical effect is that it can significantly improve the contact ratio of the gears. A higher contact ratio means that during the gear meshing process, the number of teeth pairs participating in meshing simultaneously increases, thus more effectively reducing the pressure pulsation and making the material conveying more smooth and uniform. At the same time, this helix angle range can also reduce the axial force. The smaller axial force reduces the load on the axial support structure of the pump body 1, reduces the wear and fatigue of the axial components, and improves the overall stability and service life of the pump body. In addition, the appropriate helix angle helps to improve the efficiency of gear transmission, reduce energy loss, and further optimize the working performance of the pump.

[0039] Furthermore, the ratio of the tooth width to the pitch diameter of the first helical gear 2 and the second helical gear 3 is between 0.2 - 0.4.

[0040] In this embodiment, when the ratio of the tooth width to the pitch diameter of the first helical gear 2 and the second helical gear 3 is between 0.2 - 0.4, the technical effect is that it can optimize the load distribution on the tooth surface. A reasonable ratio makes the load borne by the tooth surface more uniform, avoiding the situation of excessive local stress, thereby reducing the wear and fatigue damage of the tooth surface. This helps to extend the service life of the gears, ensure the stability and reliability of the gears during long-term operation, reduce the maintenance and replacement costs caused by tooth surface damage, and at the same time ensure the stable performance of the pump during long-term use, and can continuously and effectively convey the enema material.

[0041] Furthermore, the normal pressure angle of the first helical gear 2 and the second helical gear 3 is 22° - 25°.

[0042] In this embodiment, when the normal pressure angle of the first helical gear 2 and the second helical gear 3 is set to 22°-25°, the technical effect is that it can change the force distribution on the tooth surface. Compared with the traditional 20° pressure angle, this larger pressure angle can, to a certain extent, improve the load-bearing capacity of the gear, enabling it to withstand greater loads without failure. At the same time, it can also improve the transmission efficiency, reduce the energy loss during transmission, and make the pump more energy-efficient and efficient during operation. This helps to enhance the working performance and reliability of the entire pulsation-free helical pump, extend its service life, and reduce the operating cost.

[0043] Furthermore, the addendum coefficient of the first helical gear 2 and the second helical gear 3 is 1.1-1.3. Appropriately increasing the addendum coefficient can increase the addendum thickness, improve the anti-wear ability of the addendum, and thus extend the service life of the gear.

[0044] In this embodiment, when the addendum coefficient of the first helical gear 2 and the second helical gear 3 is 1.1-1.3, the technical effect is that the addendum thickness is appropriately increased. This increased addendum thickness can improve the anti-wear ability of the addendum, making the addendum part of the gear less likely to fail due to wear during long-term operation. Thus, it effectively extends the service life of the gear, reduces the decline in gear accuracy and transmission failures caused by addendum wear, ensures the stability and reliability of the pulsation-free helical pump during long-term use, and reduces the frequency and cost of maintaining and replacing gears.

[0045] Furthermore, the backlash coefficient of the first helical gear 2 and the second helical gear 3 is 0.3-0.4. A larger backlash coefficient can provide more storage space for lubricating oil, which helps to improve the lubrication conditions of the tooth surface, reduce wear and heat generation.

[0046] In this embodiment, when the backlash coefficient of the first helical gear 2 and the second helical gear 3 is 0.3-0.4, the technical effect is that it can provide more storage space for lubricating oil. Such a larger backlash can accommodate more lubricating oil, and when the gear rotates, the lubricating oil can lubricate the tooth surface more fully. It helps to improve the lubrication conditions of the tooth surface, reduce the friction and wear between the tooth surfaces, reduce the heat generated by friction, and thus reduce the heat generation phenomenon. This is beneficial to maintaining the good working state of the gear, extending the service life of the gear, improving the operation stability and reliability of the pump, and reducing the maintenance cost and failure rate.

[0047] Furthermore, the ratio of the pitch diameter of the first helical gear 2 to the pitch diameter of the second helical gear 3 is between 1.2-1.5. By limiting the ratio of the pitch diameters of the two gears, the flow characteristics of the pump are optimized, and the working efficiency of the pump is improved.

[0048] In this embodiment, when the ratio of the pitch diameter of the first helical gear 2 to the pitch diameter of the second helical gear 3 is between 1.2 and 1.5, the technical effect is that it can optimize the flow characteristics of the pump. By reasonably limiting the ratio of the pitch diameters of the two gears, the pump can more accurately control the flow rate and pressure of the material during operation. This helps to improve the working efficiency of the pump, enables the pump to more efficiently transport the enema material under different working conditions, reduces energy loss, and at the same time ensures the stability and accuracy of the transportation process, meeting various requirements for material transportation in enema production.

[0049] Furthermore, the tooth roots 204 of the first helical gear 2 and the second helical gear 3 are configured such that the transition curve adopts an optimized involute-arc transition. This transition form can reduce the stress concentration coefficient at the tooth roots 204 compared to the traditional involute transition, and improve the fatigue resistance of the gears.

[0050] The center distance tolerance of the first helical gear 2 and the second helical gear 3 is within ±0.1 mm. Precise control of the center distance tolerance helps to ensure the correct meshing of the gears, and reduces vibration and pressure pulsation caused by center distance deviation.

[0051] In this embodiment, for the tooth root 204 transition curve of the first helical gear 2 and the second helical gear 3, an optimized involute-arc transition is adopted: the technical effect is that it can significantly reduce the stress concentration coefficient at the tooth roots 204. This optimized transition form avoids excessive stress concentration at the tooth roots, thereby improving the fatigue resistance of the gears, extending the service life of the gears, and making the gears less likely to have faults such as tooth root fracture during long-term operation.

[0052] For the center distance tolerance of the first helical gear 2 and the second helical gear 3 within ±0.1 mm: the technical effect is that precise control of the center distance tolerance can ensure the correct meshing of the gears. It reduces poor meshing caused by center distance deviation, reduces vibration and pressure pulsation caused thereby, improves the smoothness and reliability of the pump operation, and ensures the stability and accuracy of material transportation.

[0053] In this embodiment, the surface roughness Ra of the tooth surfaces of the first helical gear 2 and the second helical gear 3 is between 0.8 and 1.6 μm. The lower surface roughness can reduce the friction coefficient between the tooth surfaces, reduce energy loss, and improve the overall efficiency of the pump.

[0054] In this embodiment, the tooth thickness deviation of the first helical gear 2 and the second helical gear 3 is within ±0.05 mm. Strict control of the tooth thickness deviation can improve the manufacturing accuracy of the gears, ensure good meshing between the gears, and reduce pressure pulsation caused by tooth thickness deviation.

[0055] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the spirit and scope of the technical solutions of the present invention, and they should all be covered within the scope of the claims of the present invention.

Claims

1. A pulsation-free helical gear pump, characterized in that, Including: A pump body (1), the pump body (1) having a pump chamber (101), the pump chamber (101) having an inlet (102) and an outlet (103); A first helical gear (2) and a second helical gear (3), the first helical gear (2) and the second helical gear (3) both being rotatably arranged in the pump chamber (101) and meshing with each other, having a pump material gap (201) therebetween, the inlet (102) facing the pump material gap (201), the pump material gap (201) facing the outlet (103), wherein the first helical gear (2) and the second helical gear (3) both have a plurality of helical teeth (202) arranged circumferentially, the upper end of the helical tooth (202) being a tooth tip (203) and the lower end being a tooth root (204), and the helical teeth (202) being configured such that before the tooth roots (204) of the first helical gear (2) and the second helical gear (3) that mesh with each other disengage, there is still at least one tooth tip (203) of the first helical gear (2) and the second helical gear (3) that meshes.

2. The pulsation-free helical gear pump according to claim 1, characterized in that, The helical teeth (202) are configured such that before the tooth roots (204) of the first helical gear (2) and the second helical gear (3) that mesh with each other disengage, there are still 1 - 4 tooth tips (203) of the first helical gear (2) and the second helical gear (3) that mesh.

3. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The module of the first helical gear (2) and the second helical gear (3) is between 1.5 - 5 mm, and the module of the first helical gear (2) and the second helical gear (3) is the same.

4. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The helix angle β of the first helical gear (2) and the second helical gear (3) is 15° - 30°.

5. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The ratio of the tooth width to the pitch diameter of the first helical gear (2) and the second helical gear (3) is between 0.2 - 0.

4.

6. The non-pulsating helical gear pump according to claim 1 or 2, characterized in that The normal pressure angle of the first helical gear (2) and the second helical gear (3) is 22° - 25°.

7. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The addendum coefficient of the tooth tips (203) of the first helical gear (2) and the second helical gear (3) is 1.1 - 1.

3.

8. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The clearance coefficient of the first helical gear (2) and the second helical gear (3) is 0.3 - 0.

4.

9. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The ratio of the pitch diameter of the first helical gear (2) to the pitch diameter of the second helical gear (3) is between 1.2 - 1.

5.

10. The pulsation-free helical gear pump according to claim 1 or 2, characterized in that, The tooth roots (204) of the first helical gear (2) and the second helical gear (3) are configured such that the transition curve adopts an optimized involute - arc transition.

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