Rack and pinion guide structure and electric motor for pumps

Abstract

This utility model relates to the field of electric motor technology, specifically disclosing a rack guide structure, including a guide sleeve with a guide channel. The cross-sectional shape of the guide channel is non-circular or non-arc, and the guide wall of the guide channel includes at least one planar segment. The guide channel is used to cooperate with an anti-rotation part on the rack. The cross-sectional shape of the anti-rotation part is adapted to the shape of the guide channel, allowing the rack to reciprocate along the guide channel. A pump electric motor includes a motor body, a gear, and a rack. The motor body drives the gear to rotate, and the rack meshes with the gear, serving as the reciprocating drive source for the pump body. It also includes the aforementioned rack guide structure. The guide sleeve in the rack guide structure is fixedly installed on the housing of the motor body, and the anti-rotation part of the rack cooperates with the guide channel of the guide sleeve. This solution addresses the problem of easy wear caused by rack deflection or tilting in current rack-output motors.

Description

Technical Field

[0001] This utility model relates to the field of electric motor technology, specifically to a rack and pinion guide structure and an electric motor for pumps. Background Technology

[0002] Positive displacement pumps, as devices capable of precisely controlling the flow of fluids, play a vital role in industrial production, especially in the field of adhesive application, where they can precisely apply or spray adhesives (such as epoxy resin, silicone, UV adhesive, etc.) to specific locations on the workpiece.

[0003] Currently, the core power component of widely used adhesive application equipment is a rack and pinion positive displacement pump driven by an electric motor (such as the reciprocating positive displacement pump with an electric reverse motor, patent publication number CN103814213A). The basic working principle of this pump is as follows: the output shaft of the electric motor drives the gear to rotate through a coupling or reduction mechanism. The gear meshes with a rack slidably connected within the motor housing, converting the motor's rotational motion into the rack's linear reciprocating motion. In other words, the electric motor's output is ultimately via the rack. The rack is typically directly or indirectly connected to a piston or diaphragm within the pump body, thus forming the pump's power input. The reciprocating motion of the rack causes periodic changes in the pump chamber's volume, thereby completing the constant-volume intake and discharge process of the fluid and achieving control over the adhesive output.

[0004] However, this traditional gear and rack drive structure suffers from abnormal wear and even brittle fracture of the gears and rack in actual operation, especially under high-load, high-frequency continuous working conditions. Specifically, the teeth on the gears are prone to fatigue cracks and eventually break; at the same time, the teeth of the rack that mesh with them also experience wear.

[0005] The inventors analyzed the data and discovered that the rack's dynamic stability during reciprocating motion was insufficient, leading to uneven loading of the meshing pair. Ideally, the center distance between the gear and the rack should remain constant, with full-width contact during meshing. However, in actual structures, to meet the requirements of the rack as the power input end of the pump, it is designed as a combination of a cylindrical shaft and toothed sections (except for the specific toothed section, the outer circumference of the rest of the rack is usually machined into a smooth arc (cylindrical) surface). While this cylindrical surface structure facilitates the installation of sealing rings to achieve dynamic sealing during reciprocating motion and prevent fluid leakage, it also results in extremely poor circumferential anti-rotation capability of the rack.

[0006] When the motor is operating under ideal conditions or low load, the meshing force between the gear and rack is sufficient to maintain the translation of the rack, and its slight deflection tendency can be constrained by the center distance tolerance. However, when the motor runs for too long or encounters a momentary overload (such as a sudden change in adhesive viscosity or a minor blockage in the pipeline), the force acting on the rack becomes complex and unbalanced. Especially when the rack reverses direction, the force direction between the gear and rack changes, and the rack is prone to oscillate along the axis under a large impact. At this time, the traditional cylindrical guide structure cannot provide effective torque resistance, and the rack will deflect or tilt under the action of the tangential component of the meshing force. Once deflection or tilting occurs, the meshing between the gear and rack changes from ideal contact to partial line contact or even point contact, resulting in wear. Utility Model Content

[0007] The present invention aims to provide a rack and pinion guide structure to solve the problem that the rack in the current rack and pinion output motor is prone to deflection or tilting, which leads to easy wear.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] A rack and pinion guide structure includes a guide sleeve, on which a guide channel is provided. The cross-sectional shape of the guide channel is non-circular or non-arc, and the guide wall of the guide channel includes at least one planar segment.

[0010] The guide channel is used to cooperate with the anti-rotation part on the rack. The cross-sectional shape of the anti-rotation part is adapted to the shape of the guide channel, so that the rack moves back and forth along the guide channel.

[0011] The principle and advantages of this solution are as follows: When the rack reciprocates, the anti-rotation part of the rack must reciprocate within a guide channel with at least one planar segment. By utilizing the guide channel with a non-circular cross-section, the deflection or tilt of the rack is restricted. Thus, even if a torsional torque is generated due to the meshing of the rack and gear, the rack can be forced to maintain linear motion under the rack guide structure. This solves the problem of meshing wear or even tooth breakage caused by rack deflection, and helps to improve the service life of the gear pair under gear-rack meshing.

[0012] Preferably, as an improvement, the guide channel has a U-shaped or V-shaped structure. This solution has a simple structure, is easy to process, and takes into account manufacturing costs while ensuring anti-rotation effect.

[0013] Preferably, as an improvement, the guide wall surface of the guide channel is provided with a wear-resistant layer to improve the wear resistance and service life of the guide channel.

[0014] Preferably, as an improvement, the guide wall surface of the guide channel is distributed with multiple lubrication grooves. The lubrication grooves in this solution are used to store and transport lubricating oil, effectively reducing frictional resistance and wear, and ensuring the smooth operation of the rack reciprocating movement.

[0015] Preferably, as an improvement, the guide wall is also provided with crisscrossing grid grooves, which are connected to the lubrication grooves. The spacing between adjacent grooves in the grid grooves is smaller than the spacing between adjacent lubrication grooves. This solution forms a dense lubrication network through the grid grooves, and uses capillary action to evenly diffuse the lubricating oil to the entire guide wall, which helps to eliminate lubrication dead zones.

[0016] Preferably, as an improvement, the depth of the mesh groove is less than the depth of the lubrication groove. In this design, the deeper lubrication groove serves as the main storage and inflow area for lubricating oil, while the shallower mesh groove is mainly used for the uniform diffusion of lubricating oil in the guide channel, thereby achieving efficient lubrication while maintaining structural rigidity to the maximum extent.

[0017] This utility model also provides an electric motor for a pump, including a motor body, a gear and a rack. The motor body drives the gear to rotate, and the rack meshes with the gear. The rack serves as a reciprocating drive source for the pump body. It also includes the rack guide structure, in which a guide sleeve is fixedly installed on the housing of the motor body, and the anti-rotation part of the rack cooperates with the guide channel of the guide sleeve.

[0018] Preferably, as an improvement, the rack includes an engaging section and a cylindrical section along the axial direction. The teeth and anti-rotation part of the rack are formed in the engaging section, and the cylindrical section is used to insert into the pump body and serve as the reciprocating drive source of the pump body.

[0019] This solution, through the cooperation of the guide sleeve and the rack anti-rotation part, limits the deflection and tilting of the rack caused by force, ensuring that the gear and rack are always in a good meshing state. This greatly avoids failures such as tooth breakage and abnormal wear, and helps extend the service life and maintenance cycle of the electric motor and pump body. Attached Figure Description

[0020] Figure 1 This is a three-dimensional schematic diagram of an electric motor for a pump without a housing in the prior art.

[0021] Figure 2 This is a cross-sectional view of the electric motor for pumps in an embodiment of the present invention, taken along the length of the rack at the rack position (the figure shows the housing of the motor body).

[0022] Figure 3 for Figure 2 A cross-sectional view along the output shaft axis at the meshing position of the rack and gear.

[0023] Figure 4 for Figure 2A three-dimensional structural diagram of the rack in the diagram.

[0024] Figure 5 for Figure 4 A schematic diagram of the three-dimensional structure after rotation.

[0025] Figure 6 for Figure 2 Top view of the rack and pinion guide structure.

[0026] Figure 7 for Figure 2 Front view of the rack and pinion guide structure.

[0027] Figure 8 for Figure 7 A schematic diagram of direction A.

[0028] Figure 9 This is a three-dimensional structural diagram of the rack guide structure and the rack in an embodiment of the present invention.

[0029] Figure 10 for Figure 9 A bottom view.

[0030] The reference numerals in the accompanying drawings include: motor body 10, reduction mechanism 101, gear 20, rack 30, meshing section 31, anti-rotation part 311, cylindrical section 32, guide sleeve 1, lubrication groove 11, and mesh groove 12. Detailed Implementation

[0031] The following detailed description illustrates the specific implementation methods:

[0032] The basic implementation examples are as follows: Figures 2 to 10 As shown.

[0033] An electric motor for a pump includes a motor body 10, a gear 20, a rack 30, and a rack guide structure mounted on the housing of the motor body 10. A reduction mechanism 101 on the motor body 10 drives the gear 20 on the output shaft to rotate. (The motor body 10 with the reduction mechanism 101 in this embodiment is the same as the motor body 10 in the prior art; in both cases, the motor shaft of the motor body 10 provides the power source for the reduction mechanism 101, and the power is reduced in speed by the reduction mechanism 101 and then output from the output shaft to the rack 30 via the gear 20. This is prior art; the detailed reduction mechanism 101 is not described here.) Figure 3In the mid-section view, one of the large gears of the reduction mechanism 101 mounted on the output shaft is exactly cut off. The rack 30 meshes with the gear 20. The rack 30 includes a meshing section 31 and a cylindrical section 32 along the axial direction. The meshing section 31 of the rack 30 is formed with teeth and an anti-rotation part 311 opposite to the teeth. The cylindrical section 32 is used to insert into the pump body and serve as the reciprocating drive source of the pump body. The rack guide structure is used to guide and limit the reciprocating linear motion of the meshing section 31.

[0034] Specifically, the rack guide structure includes a guide sleeve 1, on which a guide channel is machined. The cross-sectional shape of the guide channel is non-circular or non-arc, and the guide wall of the guide channel includes at least one planar segment. In this embodiment, the guide channel is U-shaped.

[0035] The guide channel is used to cooperate with the anti-rotation part 311 on the rack 30. The cross-sectional shape of the anti-rotation part 311 is adapted to the shape of the guide channel, so that the rack 30 moves back and forth along the guide channel. In this embodiment, the anti-rotation part 311 is also U-shaped.

[0036] The guide wall surface of the guide channel is provided with a wear-resistant layer. Multiple lubrication grooves 11 are machined on the guide wall surface, and crisscrossing grid grooves 12 are also machined on the guide wall. The grid grooves 12 are connected to the lubrication grooves 11. The spacing between adjacent grooves in the grid groove 12 is smaller than the spacing between adjacent lubrication grooves 11, and the depth of the grid groove 12 is smaller than the depth of the lubrication groove 11. In this embodiment, the lubrication grooves 11 serve as the main storage and inflow area for lubricating oil. The shallow grid grooves 12 are mainly used for the uniform diffusion of lubricating oil within the guide channel, reducing the probability of lubrication dead zones and achieving efficient lubrication while maximizing structural rigidity.

[0037] In this embodiment, after the motor body 10 is started, the rack 30 is driven by the gear 20 to reciprocate. Because the anti-rotation part 311 of the rack 30 must reciprocate within the guide channel with at least one planar section, the non-circular cross-section of the guide channel restricts the deflection or tilt of the rack 30. Even if the rack 30 and the gear 20 generate a torsional torque due to meshing, the rack 30 can be forced to maintain a straight motion under the rack guide structure. This solves the problem of meshing wear or even tooth breakage caused by the deflection of the rack 30, and helps to improve the service life of the gear 20 pair under the meshing of the gear 20 and rack 30. This helps to extend the service life and maintenance cycle of the electric motor and pump body.

[0038] In addition, since the rack 30 has both a meshing section 31 with an anti-rotation part 311 and a cylindrical section 32 inserted into the pump body, and the cylindrical section 32 is used as the reciprocating drive source of the pump body after passing through the sealing guide ring fixedly installed on the housing, the reciprocating movement of the rack 30 is guided by both the guide sleeve 1 and the sealing guide ring, thereby ensuring that even if the rack 30 is long, it can reciprocate smoothly without deviation.

[0039] The above descriptions are merely embodiments of this utility model. Commonly known technical solutions and / or characteristics are not described in detail here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the technical solution of this utility model. These modifications and improvements should also be considered within the scope of protection of this utility model, and will not affect the effectiveness of the implementation of this utility model or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. A rack and pinion guide structure, comprising a guide sleeve, wherein the guide sleeve is provided with a guide channel, characterized in that: The cross-sectional shape of the guide channel is non-circular or non-arc, and the guide wall of the guide channel includes at least one planar segment; the guide channel is used to cooperate with the anti-rotation part on the rack, and the cross-sectional shape of the anti-rotation part is adapted to the shape of the guide channel, so that the rack moves back and forth along the guide channel.

2. The rack guide structure according to claim 1, characterized in that: The guide channel has a U-shaped or V-shaped structure.

3. The rack and pinion guide structure according to claim 1, characterized in that: The guide wall surface of the guide channel is provided with a wear-resistant layer.

4. The rack and pinion guide structure according to claim 1, characterized in that: The guide wall surface of the guide channel has multiple lubrication grooves.

5. The rack and pinion guide structure according to claim 4, characterized in that: The guide wall is also provided with crisscrossing grid grooves, which are connected to the lubrication grooves. The distance between adjacent grooves in the grid groove is smaller than the distance between adjacent lubrication grooves.

6. The rack guide structure according to claim 5, characterized in that: The depth of the mesh groove is less than the depth of the lubrication groove.

7. An electric motor for a pump, comprising a motor body, a gear, and a rack, wherein the motor body drives the gear to rotate, the rack meshes with the gear, and the rack serves as a reciprocating drive source for the pump body, characterized in that, It also includes the rack guide structure as described in any one of claims 1-6, wherein the guide sleeve in the rack guide structure is fixedly installed on the housing of the motor body, and the anti-rotation part of the rack cooperates with the guide channel of the guide sleeve.

8. The electric motor for pumps according to claim 7, characterized in that: The rack includes an engagement section and a cylindrical section along the axial direction. The teeth and anti-rotation part of the rack are formed in the engagement section, and the cylindrical section is used to insert into the pump body and serve as the reciprocating drive source of the pump body.

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