CN111408999A

CN111408999A - Pressing plate flange and angle grinder with same

Info

Publication number: CN111408999A
Application number: CN201910693698.2A
Authority: CN
Inventors: 孙益民; 钟红风; 张士松
Original assignee: Positec Power Tools Suzhou Co Ltd
Current assignee: Positec Power Tools Suzhou Co Ltd
Priority date: 2019-01-08
Filing date: 2019-07-30
Publication date: 2020-07-14

Abstract

The invention discloses a pressure plate flange and an angle grinder with the same, wherein the pressure plate flange is provided with an annular body with a through hole, and the annular body comprises: the flange cover and the flange seat of cooperation installation, the flange seat is formed with confined annular raceway with the flange cover cooperation, be provided with the spin in the annular raceway, this physical ability of annular is installed on the output shaft through detachable shaft hole complex mode, makes the output shaft can change different clamp plate flanges as required. The pressure plate flange and the angle grinder with the pressure plate flange provided by the invention can effectively slow down the vibration generated by grinding the cutting sheet under different working conditions, thereby better meeting the use requirements of users.

Description

Pressing plate flange and angle grinder with same

Technical Field

The invention relates to the technical field of electric tools, in particular to a pressure plate flange and an angle grinder with the same.

Background

An angle grinder, also known as a grinder or a disc grinder, is a portable electric tool for cutting and grinding glass fiber reinforced plastics.

The angle grinder is generally provided with: the grinding machine comprises a machine shell, a driving device accommodated in the machine shell, a switch electrically connected with the driving device, and a grinding sheet provided with rotary power by the driving device. The driving device and the grinding and cutting sheet can be connected through an output shaft, and the grinding and cutting sheet can be limited through the upper flange and the lower flange. When the angle grinder is electrified for use, the driving device transmits the rotating force of the lower flange to the output shaft, and the lower flange drives the grinding and cutting piece to synchronously rotate at high speed under the action of friction force. The grinding and cutting sheet rotating at high speed can carry out operations such as grinding, cutting, derusting, polishing and the like on corresponding materials.

In the operation process, an operator holds the handle and starts the angle grinder through the starting button, so that the grinding and cutting piece rotates at a high speed. However, the abrasive cut pieces rotating at high speed are liable to generate vibrations. If the vibration is not weakened in an effective mode, on one hand, the operator feels discomfort such as hand numbness after long-time operation, so that the operation quality is reduced, and even the physical health of the operator is affected; on the other hand, the grinding slice is in a vibration state for a long time and is easy to damage, and the service life is shortened.

Disclosure of Invention

In order to overcome the defects of the prior art, the invention provides the pressure plate flange and the angle grinder with the pressure plate flange, which can effectively slow down the vibration generated by grinding the cutting piece under different working conditions, thereby better meeting the use requirements of users.

The above object of the present invention can be achieved by the following technical solutions:

A platen flange having an annular body with a through-hole, the annular body being mountable on an output shaft by way of a detachable shaft hole fit, the annular body comprising: the flange cover and the flange seat are installed in a matched mode, the flange seat and the flange cover are matched to form a closed annular rolling way, and a rolling ball is arranged in the annular rolling way.

Furthermore, the pressure plate flange is provided with a centering mechanism, the centering mechanism is arranged in the through hole, and when the pressure plate flange is connected with the output shaft, the centering mechanism can ensure that the pressure plate flange rotates around the axis of the output shaft.

In a preferred embodiment, the centering mechanism comprises: the shaft centering element is arranged in the through hole and can elastically deform in the radial direction, and the outer side of the shaft centering element is abutted against the side wall of the through hole.

In a preferred embodiment, the centering element is an elastomer having an overall ring shape with an inner ring surface and an outer ring surface, the inner ring surface being concentric with the outer ring surface.

In a preferred embodiment, the centering element is a metal elastic sheet, and a telescopic part is arranged on the metal elastic sheet, and the telescopic part has opposite outer top ends, and the outer top ends are abutted against the side wall of the through hole.

In a preferred embodiment, the centering element has an upper end surface and a lower end surface opposite to each other, and a height of the centering element from the upper end surface to the lower end surface is smaller than a height of the through hole in the direction of the rotation axis.

In a preferred embodiment, the ball is disposed in the raceway in a clearance fit with a lateral clearance therebetween; the flange cover is provided with a first groove used for being matched with the rolling ball, at least the middle part of the cross section of the first groove is provided with an arc section, the circle center corresponding to the arc section projects to the horizontal plane where the center of the rolling ball is located, and the distance between the circle center and the center of the rolling ball is within the range of the lateral clearance.

In a preferred embodiment, the cross-section of the first groove comprises: the flange seat is provided with a second groove matched with the rolling ball, the cross section of the second groove is a rectangle with a fillet, and the two sides of the rectangle are coplanar with the extension lines of the trimming edges.

In a preferred embodiment, the arc of the circular arc segment is greater than 60 degrees.

In a preferred embodiment, the number of balls is an even number.

In a preferred embodiment, the number of said balls is 6.

In a preferred embodiment, the flange seat and the flange cover are in interference fit, a first sealing ring and a second sealing ring are further arranged at the positions where the flange seat and the flange cover are matched, and an assembly cavity for mounting the first sealing ring and the second sealing ring is formed by matching the flange seat and the flange cover; the size of the assembly cavity in a direction along the output shaft is no greater than the thickness of the first and second seal rings.

In a preferred embodiment, the first and second seal rings are compressed to 70% along the axial thickness of the output shaft after being fitted into the fitting cavity.

In a preferred embodiment, the first sealing ring and the second sealing ring have a height difference in a height direction.

In a preferred embodiment, the outer edge of the flange cover is provided with a first matching portion, the outer edge of the flange seat is provided with a second matching portion, and the first matching portion and the second matching portion are engaged to form a riveting structure.

In a preferred embodiment, the flange seat has an inner ring portion and an outer ring portion which are opposite to each other, the inner ring portion has a larger contact height with the flange cover than the outer ring portion, and the inner ring portion is configured to cooperate with the flange cover to form an interference which is larger than the interference formed by the outer ring portion with the flange cover.

An angle grinder is provided with an output shaft and at least two kinds of pressure plate flanges, wherein the output shaft is alternatively matched with the at least two kinds of pressure plate flanges in a detachable mode and can drive the pressure plate flanges to rotate coaxially, and the at least two kinds of pressure plate flanges comprise the pressure plate flanges in any one of the above embodiments.

Further, the at least two platen flanges further include a first platen flange having only an integral annular body.

In a preferred embodiment, a connecting portion is arranged on a side wall of the through hole, a first mounting portion matched with the connecting portion is arranged on the output shaft, and the connecting portion and the first mounting portion are matched to form a transmission structure for transmitting torque.

In a preferred embodiment, an annular cavity is formed between a side wall of the output shaft and a side wall of the through hole, and the centering mechanism includes: the inner side of the centering shaft element is abutted against the side wall of the output shaft, and the outer side of the centering shaft element is abutted against the side wall of the through hole.

In a preferred embodiment, the side wall of the output shaft is provided with an external conical surface with a preset taper angle, the side wall of the through hole is provided with an internal conical surface with the same taper angle as the external conical surface, and the external conical surface is matched and attached with the internal conical surface to form the centering mechanism.

In a preferred embodiment, the taper angle of the outer or inner conical surface is greater than 10 degrees.

When the grinding sheet is replaced in the angle grinder with the balance flange in the prior art, only the grinding sheet and a top plate flange on the upper portion of the grinding sheet are replaced, and a pressing plate flange below the grinding sheet does not influence the disassembly and the assembly of the grinding sheet, so the pressing plate flange is generally arranged on an output shaft in a fixed connection mode. And the clamp plate flange that this application provided sets up on the output shaft through dismantling shaft hole complex mode, when the user changes the mill section, it can select suitable clamp plate flange according to the balance performance of mill section itself to can all reach best shock attenuation effect under the operating mode of difference.

Furthermore, the pressure plate flange is provided with the centering mechanism, after the pressure plate flange is connected with the output shaft, the geometric center line of the pressure plate flange can be ensured to coincide with the axis of the output shaft or tend to coincide with the axis of the output shaft, and therefore a better damping effect can be achieved. Particularly, when the pressure plate flange and the output shaft have a certain fit tolerance, a centering mechanism is arranged between the pressure plate flange and the output shaft, so that a remarkable damping effect can be achieved.

Drawings

The invention is further described with reference to the following figures and embodiments.

FIG. 1 is an exploded view of an angle grinder according to an embodiment of the present disclosure;

FIG. 2 is a schematic illustration of the platen flange in an embodiment of the present application;

3 FIG. 3 3 3 is 3 a 3 sectional 3 view 3 A 3- 3 A 3 of 3 the 3 angle 3 grinder 3 of 3 FIG. 3 2 3 with 3 the 3 platen 3 flange 3 installed 3; 3

FIG. 4 is an exploded schematic view of the platen flange of FIG. 3;

FIG. 5 is a cross-sectional view of an angle grinder in another embodiment of the present application;

FIG. 6 is an exploded schematic view of the platen flange of FIG. 5;

FIG. 7 is a schematic view of the structure of the centering element of FIG. 5;

FIG. 8 is a cross-sectional view of an angle grinder in yet another embodiment of the present application;

FIG. 9 is a B-B cross-sectional view of the angle grinder of FIG. 3 with the platen flange installed;

FIG. 10 is a cross-sectional view of a platen flange of the present application

Fig. 11 is a partially enlarged schematic view of the position of the platen flange I in fig. 3.

Description of reference numerals:

10. A platen flange; 10', a first platen flange; 101. a flange seat; 1010. a second groove; 1011. a friction surface of the flange; 1012. an axial positioning part; 1013. a second mating portion; 102. a connecting portion; 103. rolling a ball; 104. a first seal ring; 105. a second seal ring; 106. a flange cover; 1061. a first groove; 1062. a first mating portion; 1063. an inner ring portion; 1064. an outer ring portion; 107. a raceway; 108. a centering element; 108', a centering mechanism; 1081. an outer tip; 1082. an inner top end; 20. a whole machine; 201. a power source; 202. a housing; 203. a shield; 204. an output shaft; 2042. a first mounting portion; 2041. a second mounting portion; 205. a top plate flange; 30. grinding and slicing; 40. an auxiliary handle.

Detailed Description

The technical solutions of the present invention will be described in detail with reference to the accompanying drawings and specific embodiments, it should be understood that these embodiments are merely illustrative of the present invention and are not intended to limit the scope of the present invention, and various equivalent modifications of the present invention by those skilled in the art after reading the present invention fall within the scope of the appended claims.

It will be understood 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 the like as used herein are for illustrative purposes only and do not denote a unique embodiment.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein in the description of the present application is for the purpose of describing particular embodiments only and is not intended to be limiting of the 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 overcome various problems caused by vibration of the grinding chips when the angle grinder is used, the angle grinder, particularly the lower flange portion, may be improved. For example, an automatic balancing device may be provided on the angle grinder. The automatic balancing device is mainly provided with an annular rolling ball cavity, and a plurality of movable rolling balls are arranged in the annular rolling ball cavity. In the high-speed operation process, the internal rolling ball automatically finds a balance point by centrifugal force, so that the vibration of the machine is reduced, the service life of the grinding slice is prolonged, and the hand numbness caused by vibration of an operator is avoided.

However, the applicant found that: the automatic balancing device of the angle grinder only plays a certain cushioning effect on the working condition with large unbalance amount, does not play a role in grinding slices (such as metal cutting slices, small grinding slices and the like) with good balance per se, and even can aggravate vibration. The main reasons were analyzed as follows: the rolling balls playing a balancing role are respectively and discretely distributed in the rolling way, and the distribution of the rolling balls is not necessarily centrosymmetric in the rotation process of the output shaft, so that the rolling balls which are not uniformly distributed can aggravate vibration when no unbalance or small balance exists.

Referring to fig. 1 to 4 in combination, a platen flange 10 is provided according to an embodiment of the present application. The platen flange 10 has an annular body with a through hole, the annular body including: the flange cover 106 and the flange seat 101 are installed in a matching mode, the flange seat 101 and the flange cover 106 are matched to form a closed annular raceway 107, and a rolling ball 103 is arranged in the annular raceway 107. The pressure plate flange 10 can be installed on the output shaft 204 in a detachable shaft hole matching mode, so that the output shaft can be replaced by different pressure plate flanges as required.

When the grinding sheet is replaced in the angle grinder with the balance flange in the prior art, only the grinding sheet and a top plate flange on the upper portion of the grinding sheet are replaced, and a pressing plate flange below the grinding sheet does not influence the disassembly and the assembly of the grinding sheet, so the pressing plate flange is generally arranged on an output shaft in a fixed connection mode. And the clamp plate flange 10 that this application provided sets up on output shaft 204 through detachable shaft hole cooperation mode, when the user changes the section of grinding, it can select suitable clamp plate flange 10 according to the balance performance of grinding section 30 itself to can all reach best shock attenuation effect under the operating mode of difference.

In the present embodiment, the platen flange 10 is a platen flange 10 having a self-balancing function. The pressure plate flange 10 is installed on the output shaft 204 of the power tool through a detachable shaft hole mode, so that the output shaft 204 can be replaced by different pressure plate flanges according to needs, wherein the different pressure plate flanges can be the pressure plate flange 10 with the self-balancing function or a conventional pressure plate flange 10'. In particular, the power tool may comprise a saw-type tool, such as an electric circular saw, a sanding-type tool (e.g., an angle grinder, etc.). In the following embodiments, specific application scenarios of the platen flange 10 are mainly exemplified by an angle grinder, and other application scenarios can be referred to by analogy, which is not described herein again.

When the user need change different mill sections, can see whether need change the clamp plate flange simultaneously as required. Generally, for an abrasive cut sheet with poor balance per se, such as a large abrasive cut sheet, a non-metal abrasive cut sheet, etc., it is possible to select a pressure plate flange 10 having a self-balancing function as provided in the present application; to the better mill section of self balance, for example, metal cutting piece, small-size mill section etc. its first clamp plate flange 10' that can choose not to set up above-mentioned balanced structure to can all reach best shock attenuation effect under the operating mode of difference.

In the present embodiment, the pressure plate flange 10 having the self-balancing function may have a ring-shaped body with a through hole, which includes a flange cover 106 and a flange seat 101 fitted thereto. Wherein, the flange seat 101 and the flange cover 106 are matched to form a closed annular raceway 107, and the annular raceway 107 is internally provided with a rolling ball 103. When the platen flange 10 is installed in an angle grinder for operation, the rolling balls 103 in the annular raceway 107 can automatically find a balance point by centrifugal force during high-speed operation, thereby reducing vibration of the angle grinder. In order to ensure that the distribution of the rolling balls 103 tends to be centrosymmetric during the uniform rotation of the output shaft 204 of the angle grinder, the number of the rolling balls 103 is preferably even, and may be 4, 6 or 8, for example. Specifically, the number of the balls 103 may be adaptively adjusted according to factors such as the size of the raceway 107, and the present application is not limited thereto.

In one specific embodiment, the number of the balls 103 is 6.

When the number of the rolling balls 103 is 6, the central angles corresponding to the circular arc sections formed by sequentially attaching the 6 rolling balls 103 are less than 180 degrees. The 6 balls 103 can be symmetrically distributed about a plane of symmetry with the amount of unbalance of the platen flange 10. The angle formed between the connecting line of the end part of the arc segment and the circle center and the symmetry plane is the optimal angle. After the optimal angle is formed, the rolling ball 103 can be ensured to find a plane at the fastest speed, namely, the plane is symmetrically distributed with the unbalance amount, and the quality of the 6 rolling balls 103 can better meet the situation that the unbalance amount has larger fluctuation compared with the situation that the quality of the 6 rolling balls 103 is smaller than that of the 6 rolling balls 103. When the number of the rolling balls 103 is larger than 6, the central angle formed by the arc sections can be increased, and the rolling balls 103 at the end parts can exceed the symmetrical plane in the movement process of the rolling balls 103, so that the balancing efficiency is reduced.

Further, in order to reduce the frictional force generated when the rolling ball 103 rolls in the annular raceway 107, the annular raceway 107 may be coated with lubricating oil or grease. Further, in order to improve the sealing performance at the mating position of the flange cover 106 and the flange seat 101 in the platen flange 10, and particularly to prevent leakage of the lubricating oil through the mating position, the platen flange 10 may be further provided with a first seal ring 104 and a second seal ring 105. Referring to fig. 3 and 4, a first annular groove is formed on the outer side of the flange cover 106 and the flange seat 101, and the first annular groove is used for installing the first sealing ring 104. A second annular groove is formed on the inner side of the flange cover 106 and the flange seat 101, which second annular groove can be used for mounting said second sealing ring 105.

Further, the platen flange 10 has a centering mechanism, which may be disposed in a through hole of the ring body. When the pressure plate flange 10 is connected to the output shaft 204, the centering mechanism can ensure that the pressure plate flange 10 rotates around the axis of the output shaft 204 when the pressure plate flange 10 is connected to the output shaft 204.

Through being provided with centering mechanism, when clamp plate flange 10 is connected with output shaft 204, centering mechanism is located between cyclic annular body and the output shaft 204, and clamp plate flange 10 is under the drive of output shaft 204, and in the synchronous pivoted process with output shaft 204, the central line of clamp plate flange 10 and the axis coincidence of output shaft 204 or tend to coincide to realize the shock attenuation. Specifically, the centering mechanism may be formed by providing a centering element 108 capable of radially elastically deforming between the annular body and the output shaft 204, or may be formed by fitting both the pressure plate flange 10 and the output shaft 204.

Generally, the output shaft 204 is a homogeneous, center-symmetric rotational body, and the axis of the output shaft 204 is a rotation axis. Because the pressure plate flange 10 is connected with the output shaft 204 in a detachable hole-shaft matching manner, specifically, the pressure plate flange 10 can be sleeved outside the output shaft 204 in a small-gap matching manner to form radial positioning; while axial positioning is achieved by cooperation with the mill cut 30, the top plate flange 205, etc.

When the radial clearance formed between the output shaft 204 and the platen flange 10 is small, for example, below a preset threshold, the vibration generated when the two are engaged is not too large, and the necessity of providing a centering mechanism is not too large. However, when the radial gap formed between the output shaft 204 and the platen flange 10 is large, for example, above a predetermined threshold value, since large vibration may be generated when the two are engaged, it is necessary to provide the centering mechanism. Specifically, the preset threshold matches the diameter of the output shaft 204, and generally, the smaller the diameter of the output shaft 204 is, the smaller the preset threshold is. Preferably, the ratio of the predetermined threshold to the output shaft 204 may be between 0.2% and 1.5%. For example, when the diameter of the output shaft is 10mm, the radial clearance between the output shaft 204 and the platen flange 10 is 0.02mm to 0.15 mm. When the diameter of the output shaft 204 is 14mm, the radial clearance between the output shaft 204 and the platen flange 10 is 0.028mm to 0.21mm, and it is expected that the preset clearance is as small as possible.

In the present embodiment, when the output shaft 204 is installed in cooperation with the platen flange 10, a transmission structure is formed between the output shaft 204 and the platen flange 10, so that the rotational power provided by the driving device is transmitted to the grinding chip 30 after passing through the output shaft 204 and the platen flange 10 in sequence, thereby driving the grinding chip 30 to rotate at a high speed.

In one embodiment, the inner side wall of the flange seat 101 is provided with a connecting portion 102, the output shaft 204 is provided with a first mounting portion 2042 matched with the connecting portion 102, and the connecting portion 102 is matched with the first mounting portion 2042 for transmitting torque. Specifically, the connecting portion 102 may have a flat square shape. Accordingly, the first mounting portion 2042 may also be in the form of a flat square.

As shown in fig. 4, the connection portion 102 may be a pair of engaging portions formed on an inner sidewall of the flange base 101. Accordingly, the side wall of the output shaft 204 is provided with a mating portion matching the engaging portion at a position for mounting the flange base 101. The engaging portion and the mating portion may be in a form of planar engagement. It is to be understood that the engaging portion and the engaging portion may be in other engaging forms, and those skilled in the art can make other modifications within the spirit of the present application, and all such modifications are intended to be included within the scope of the present application as long as the functions and effects achieved by the engaging portion and the engaging portion are the same as or similar to those of the present application.

Referring to fig. 3 and 10 in combination, in the present specification, the flange base 101 has an opening for passing through the output shaft 204, and an axial positioning portion 1012 is provided on a hole wall of the opening on a side close to the flange cover 106. Specifically, the axial positioning portion 1012 may be a limit step formed on the flange seat 101. After the output shaft 204 is installed in a matching manner with the platen flange 10, the axial positioning portion 1012, the connecting portion 102 of the flange seat 101 and the flange friction surface 1011 are all disposed on the flange seat 101, and the axial thickness of the flange seat 101 is greater than that of the flange cover 106, so as to ensure that the angle grinder with the platen flange 10 has a compact structure and is reliable in operation.

In summary, in the pressure plate flange 10 with a self-balancing function provided in the embodiment of the present application, the centering mechanism is disposed in the through hole of the annular body, so that when the pressure plate flange 10 is connected to the output shaft 204 and is powered on for use, the pressure plate flange 10 can be ensured to rotate around the axis of the output shaft 204. During the rotation process, the geometric center line of the pressure plate flange 10 coincides with or tends to coincide with the rotation axis of the output shaft 204, so that a better shock absorption effect can be achieved.

For the platen flange 10, the centering mechanism may include: and the shaft centering element 108 is arranged in the through hole and can perform radial elastic deformation, and the outer side of the shaft centering element 108 is abutted against the side wall of the through hole. In particular, the centering element 108 may be an elastomer having an overall annular shape with an inner annular surface and an outer annular surface, the inner annular surface being concentric with the outer annular surface. Alternatively, the centering element 108 may be a metal elastic sheet, and a telescopic portion is disposed on the metal elastic sheet, and the telescopic portion has an opposite outer top end, and the outer top end abuts against the side wall of the through hole.

In order to ensure that the centering element 108 has sufficient deformation space when it is deformed radially, it may be necessary to deform the elastomer, which is generally annular, in an axially extending manner after it is radially compressed. To this end, the centering element 108 has opposite upper and lower end faces, and the height of the centering element from the upper end face to the lower end face is smaller than the height of the through hole in the direction of the rotation axis, thereby providing a sufficient deformation space for the given shaft center element 108.

In addition, when the ground piece 30 is replaced in the conventional angle grinder, only the ground piece 30 and the top plate flange 205 on the ground piece 30 are replaced, and the platen flange 10 below the ground piece 30 is generally provided on the output shaft 204 in a fixed connection manner because the removal and installation of the ground piece 30 are not affected. And the clamp plate flange 10 that this application provided sets up on output shaft 204 through detachable mode, when the user changes the mill section 30, it can be according to the balance performance selection suitable clamp plate flange 10 of mill section 30 itself to can all reach best shock attenuation effect under the operating mode of difference. For example, when the balance performance of the grinding and cutting sheet 30 itself is poor, the pressure plate flange 10 with the self-balancing function can be installed; when the balance of the abrasive cut-off sheet 30 itself is better, the first platen flange 10' without the self-balancing function may be optionally installed.

The angle grinder provided with the platen flange 10 will be described in detail below with reference to the specific drawings and specific usage scenarios.

As shown in fig. 1 to 8, in one embodiment, the complete machine 20 of the angle grinder may include: a body that can communicate with the power supply 201, and a working head. The main body mainly includes a housing 202 and a driving device (not shown) located in the housing 202. The driving device may be a driving motor, which is electrically connected to the power source 201. The driving device mainly provides rotary power to the working head after being electrified. The housing 202 may also be provided with an auxiliary handle 40 for easy gripping. The working head may include: an output shaft 204 connected with a driving device, and a pressure plate flange 10, a grinding and cutting sheet 30 and a top plate flange 205 which are sleeved on the output shaft 204.

In the present embodiment, the output shaft 204 is a longitudinally extending body having a first end and a second end opposite to the first end, wherein the first end of the output shaft 204 is located in the housing 202, and the second end extends out of the housing 202. The output shaft 204 is provided with a pressing plate flange 10, a grinding and cutting piece 30 and a top plate flange 205 on the side wall outside the casing 202 in sequence. Specifically, the output shaft 204 is provided with a first mounting portion 2042 for mounting the platen flange 10 and a second mounting portion 2041 for mounting the top plate flange 205.

In the present embodiment, the platen flange 10 is a platen flange 10 having a self-balancing function. Specifically, the platen flange 10 has an annular body including a flange cover 106 and a flange seat 101 which are fitted, wherein the flange seat 101 and the flange cover 106 are fitted to form a closed annular raceway 107, and the annular raceway 107 is provided with rolling balls 103. When the platen flange 10 is installed in an angle grinder for operation, the rolling balls 103 in the annular raceway 107 can automatically find a balance point by centrifugal force during high-speed operation, thereby reducing vibration of the angle grinder.

In the present embodiment, the grinding blade 30 may be a grinding wheel, a metal cutting blade, a wood cutting blade, a sponge wheel, a louver wheel, etc. in the prior art. When the angle grinder is used, the user can select the proper grinding and cutting piece 30 according to the actual requirement.

In this embodiment, the top plate flange 205 is used to press the abrasive sheet 30 in cooperation with the platen flange 10 to position the abrasive sheet 30. The top plate flange 205 may have an annular body with opposing inner and outer sidewalls. Wherein the inner side wall may be provided with threads, and the top plate flange 205 may be fixed to the second end of the output shaft 204 by means of a threaded connection. The second mounting portion 2041 may be in the form of an external thread when the top plate flange 205 is threadably secured to the output shaft 204. Of course, the top plate flange 205 may also be engaged with the output shaft 204 in other ways, and the application is not limited thereto.

In addition, referring to fig. 9, the angle grinder may further include a shield 203 covering the grinding blade 30, the shield 203 may be fixed to the working head by screws, etc., of course, the shield 203 may also be fixed by other methods, and the application is not limited in this respect. When the angle grinder is provided with the shield 203, the shield is used for preventing the angle grinder from protecting the personal safety of an operator during the working process. In particular, sparks are likely to be generated when a metal member is ground or cut, splash particles are likely to be generated when a stone material is ground or cut, and the operator can be prevented from being accidentally injured by sparks, splashes, and the like generated during the grinding process when the protective cover 203 is provided.

In the present embodiment, the platen flange 10 has a centering mechanism, which may be provided between the annular body and the output shaft 204. The centering mechanism is used for ensuring that the central line coincides with the rotation axis of the output shaft 204 in the process that the pressure plate flange 10 is driven by the output shaft 204 to synchronously rotate with the output shaft 204, so that the shock absorption is realized. Specifically, the centering mechanism may be formed by disposing the centering element 108 capable of radially elastically deforming between the pressure plate flange 10 and the output shaft 204, or by fitting the pressure plate flange 10 and the output shaft 204 together.

In one embodiment, an annular cavity is formed between the side wall of the output shaft 204 and the inner side wall of the platen flange 10, the centering mechanism is a centering element 108 which is arranged in the annular cavity and can perform radial elastic deformation, the inner side of the centering element 108 abuts against the side wall of the output shaft 204, and the outer side of the centering element 108 abuts against the inner side wall of the platen flange 10.

In the present embodiment, an annular cavity is formed between the side wall of the output shaft 204 and the inner side wall of the platen flange 10, and the annular cavity is used for arranging the centering element 108. The centering element 108 is elastically deformable at least in the radial direction. When the centering element 108 is installed in the annular cavity, the inner side of the centering element is abutted against the side wall of the output shaft 204, and the outer side of the centering element 108 is abutted against the inner side wall of the pressure plate flange 10.

In the elastically deformable centering element 108, the inner and outer walls of the centering element 108 are concentric, and the centering element 108 can elastically deform in the radial direction, so that the geometric center line of the platen flange 10 can be found when the outer wall of the centering element 108 is fitted to the inside of the platen flange 10, and the rotational center line of the output shaft 204 can be found when the inner wall of the centering element 108 is fitted to the outer wall of the output shaft 204. With sufficient rigidity of the centering element 108, the force applied to the centering element 108 installed between the output shaft 204 and the platen flange 10 is directed toward the center of the circle, i.e., the centering element 108 has the characteristic of uniform force application. By utilizing the uniform stress characteristic of the centering element 108, the geometric center line of the pressure plate flange 10 and the geometric center line of the output shaft 204 can be ensured to coincide. Since the geometric center line of the output shaft 204 coincides with the rotation center line, the geometric center line of the platen flange 10 can coincide with the rotation center line of the output shaft 204. When the geometric center line of the platen flange 10 coincides with the normal rotation center line in the output, an ideal shock absorption effect can be achieved.

Referring to fig. 3 and 4 in combination, in one embodiment, the centering element 108 is a generally annular elastomer having an inner annular surface and an outer annular surface, the inner annular surface being concentric with the outer annular surface.

In this embodiment, the centering element 108 may be a ring-shaped elastomer made of an elastic material, having an inner ring surface and an outer ring surface, the inner ring surface being concentric with the outer ring surface. In particular, the centering element 108 may be an O-ring, such as a rubber O-ring. Of course, the material of the O-ring is not limited to the above examples, and the application is not limited thereto. When the centering element 108 is made entirely of a material with good elasticity, it can be deformed not only radially but also axially. When the platen flange 10 is replaced, the axial deformation of the centering element 108 can be utilized to improve the convenience of assembly and disassembly.

Referring to fig. 5 to 7, in another embodiment, the centering element 108 is a metal elastic sheet, and the metal elastic sheet is provided with a telescopic portion, the telescopic portion has an outer top end 1081 and an inner top end 1082 opposite to each other, the outer top end 1081 abuts against the inner side wall of the annular body, and the inner top end 1082 abuts against the side wall of the output shaft 204.

In the present embodiment, the centering element 108 may be in the form of a metal elastic sheet, and an expansion portion for performing radial expansion and contraction deformation may be provided on the metal elastic sheet. Specifically, the telescopic portion may have an outer tip 1081 and an inner tip 1082 opposite to each other, the outer tip 1081 may abut against an inner side wall of the annular body, and the inner tip 1082 may abut against a side wall of the output shaft 204. When the two opposite inner tips 1082 are brought closer together, the radial dimension of the centering element 108 becomes larger; the radial dimension of the centering element 108 decreases as the opposing inner tips 1082 move away.

Specifically, the metal elastic sheet may be arranged along the circumferential direction, and the principle that the (geometric) center line of the platen flange 10 coincides with the rotation axis of the output shaft 204 is the same as that of the annular elastic body in the above embodiment, which is not described herein again. When the centering element 108 is in the form of a metal elastic sheet, it has a better rigidity with respect to an O-ring.

In one embodiment, the centering element 108 has opposite upper and lower end faces, and the height of the centering element 108 from the upper end face to the lower end face is less than the height of the annular cavity along the direction of the axis of rotation.

For a metal elastic sheet with better rigidity, the metal elastic sheet is not basically deformed along the direction of the rotation axis. In order to meet the assembly requirement, the height of the metal elastic sheet is smaller than that of the annular cavity.

While for a resilient annular elastomer, such as an O-ring, which is installed in the annular cavity between the output shaft 204 and the pressure plate flange 10, the radial dimension is over-deformed toward the axial dimension. In order to ensure that the elastomer has enough deformation space, the height of the elastomer in a natural state is smaller than that of the annular cavity.

referring to fig. 8, in another embodiment, the side wall of the output shaft 204 is provided with an external conical surface having a predetermined taper angle α, and the inner side wall of the annular body is provided with an internal conical surface having the same taper angle α as the external conical surface, and the internal conical surface forms the centering mechanism 108'.

in the present embodiment, when the side wall of the output shaft 204 and the inner side wall of the pressure plate flange 10 are provided with the conical surfaces with the same taper angle α, after the two are installed in a matching manner, it can be ensured that the geometric center line of the pressure plate flange 10 coincides with the rotation center of the output shaft 204, and when the output shaft 204 drives the pressure plate flange 10, the grinding-cutting piece 30, and the top plate flange 205 to rotate synchronously, a better damping effect can be achieved.

In this embodiment, the external conical surface and the internal conical surface may be in a form of conical surface with a circular cross section, but the external conical surface and the internal conical surface may also be in a form of conical surface with a cross section, such as a shape with a triangle cross section, a spline, etc., and the specific application is not limited in this application. When the cross section is in a non-circular shape such as a triangle or a spline, the cross section can transmit torque in addition to the centering function.

because the pressure plate flange 10 provided in the embodiment of the present application is detachably connected to the output shaft 204, the pressure plate flange 10 may need to be replaced while the grinding chip 30 is replaced under different working conditions, and in order to improve the convenience of detachment between the pressure plate flange 10 and the output shaft 204, the taper angle α of the outer conical surface or the inner conical surface is greater than 10 degrees.

when the taper angle α of the outer conical surface or the inner conical surface is less than 10 degrees, self-locking between the outer conical surface and the inner conical surface is easy to occur, so that the difficulty in detaching the pressure plate flange 10 and the output shaft 204 is increased, of course, the specific angle of the taper angle α can be adaptively adjusted according to the specific size of the matching position of the output shaft 204 and the pressure plate flange 10, the morse taper reference table and the relationship between the taper C and the taper angle α, wherein C is 2 × tg (α/2).

Referring to fig. 3 and 10, in the present specification, the ball 103 is disposed in the raceway 107 in a clearance fit manner, and a lateral clearance exists between the ball 103 and the raceway 107. The flange cover 106 is provided with a first groove 1061 used for being matched with the rolling ball 103, at least the middle part of the cross section of the first groove 1061 is provided with an arc section, the circle center corresponding to the arc section projects to the horizontal plane where the sphere center of the rolling ball 103 is located, and the distance between the circle center and the sphere center is within the range of the lateral clearance.

In this embodiment, the ball 103 and the raceway 107 are in a clearance fit, i.e., the diameter of the ball 103 is smaller than the width of the raceway 107. When the ball 103 is mounted in the raceway 107, a lateral clearance is formed between the ball 103 and the raceway 107. Specifically, the lateral gap is a small gap, which mainly ensures that the ball 103 can freely roll in the raceway 107, and the size of the lateral gap can be adaptively selected according to the dimensions of the raceway 107 and the ball 103, and the application is not particularly limited herein.

In this embodiment, the inside of the top of the flanged cap 106 is provided with a first recess 1061 for receiving part of the ball 103. Specifically, as shown in fig. 10, on the cross section of the platen flange 10, the middle of the first groove 1061 is a circular arc segment. Accordingly, the top of the first recess 1061 may be a circular arc surface corresponding to the spherical surface of the ball 103. Specifically, the circle center corresponding to the arc segment projects to the horizontal plane where the center of the rolling ball 103 is located, and the distance between the circle center and the center of the rolling ball is within the range of the lateral gap.

After the arc section is arranged in the flange cover 106, when the rolling ball 103 moves in the raceway 107, particularly in a leveling stage, a speed convex surface cannot occur, that is, the running speed of the rolling ball 103 is not easy to change suddenly, and the arc section can be used for restraining and effectively guiding the movement track of the rolling ball 103 to form a target movement track at a higher speed. The target movement track, namely the movement track of the rolling ball 103 when the pressure plate flange 10 is in a self-balancing state. When the rolling ball 103 can quickly form a target movement track, when the unbalanced saw blade is installed on the pressure plate flange 10, the unbalance amount can be quickly and efficiently counteracted by using the rolling ball 103. Further, in general, in order to reduce the frictional resistance of the rolling balls 103 in the raceway 107, a lubricating oil is usually provided in the raceway 107. After the arc-shaped section is arranged, in the process of balancing the rolling ball 103, the movement track of the rolling ball 103 can be effectively restricted, and the collision frequency of the rolling ball 103 and the raceway 107 can be effectively reduced. When the collision between the rolling ball 103 and the raceway 107 is reduced, the probability that the oil in the raceway 107 flows out from the position where the flange seat 101 and the flange cover 106 are matched after being squeezed can be effectively reduced.

As shown in fig. 10, in one embodiment, the cross-section of the first groove 1061 includes: the cutting edge is arranged on two sides of the arc section and is in tangential transition with the arc section. The flange seat 101 is provided with a second groove 1010 used for being matched with the rolling ball 103, the cross section of the second groove 1010 is a rectangle with rounded corners, and two sides of the rectangle are coplanar with the extension lines of the cutting edges.

In the present embodiment, the cut edge of the cross section of the first groove 1061 is tangent to the circular arc segment and coplanar with two sides of the rectangle of the second groove 1010. Wherein the sealing surface of the flange cover 106 and the flange seat 101 is located at the matching position of the cut edge of the first groove 1061 and the rectangular edge of the second groove 1010. During the movement of the ball 103 in the raceway 107 formed by the first groove 1061 and the second groove 1010, the impact between the ball 103 and the sealing surface can be reduced as much as possible by the structure in the raceway 107, so that the probability of oil leakage can be reduced as much as possible.

In a particular embodiment, the angle of the arc segment may be greater than 60 degrees. Specifically, when the angle of the arc segment of the first groove 1061 is larger, for example, 90 degrees, the cut edge with the arc segment may be omitted, and at this time, two sides of the rectangle on the flange seat 101 may be directly tangent to the arc segment. When the circular arc segment is between 60 degrees and 90 degrees, the cross section of the first groove 1061 on the flange cover 106 is formed by the circular arc segment and the cutting edge tangent to the circular arc segment. When the angle of the arc segment is smaller than 60 degrees, a containing space matched with the ball 103 is not easy to form in the first groove 1061, which is not beneficial to effectively guiding the movement track of the ball 103.

In one embodiment, the flange seat 101 and the flange cover 106 are in an interference fit, and a first sealing ring 104 and a second sealing ring 105 are further disposed at the positions where the flange seat 101 and the flange cover 106 are engaged. The flange seat 101 and the flange cover 106 cooperate to form a mounting cavity for mounting the first sealing ring 104 and the second sealing ring 105. The dimension of the fitting cavity in the direction along the output shaft 204 is no greater than the thickness of the first and second sealing rings 104, 105.

In this embodiment, the flange seat 101 and the flange cover 106 may be in an interference fit, and the first seal ring 104 and the second seal ring 105 are respectively provided at the positions where the flange seat 101 and the flange cover 106 are engaged, so as to ensure the sealing property at the positions where the flange seat 101 and the flange cover 106 are engaged, and prevent the lubricating fluid in the raceway 107 from flowing out from the positions where the flange seat 101 and the flange cover are engaged. Specifically, the flange seat 101 and the flange cover 106 cooperate to form an assembly cavity for mounting the first sealing ring 104 and the second sealing ring 105. The dimension of the fitting cavity in the direction along the output shaft 204 is no greater than the thickness of the first and second sealing rings 104, 105. When the dimension of the assembly cavity for mounting the first sealing ring 104 and the second sealing ring 105 in the direction of the output shaft 204 is not larger than the thickness of the first sealing ring 104 and the second sealing ring 105, the first sealing ring 104 and the second sealing ring 105 can be ensured to play a sealing role after being mounted in the assembly cavity.

Specifically, after the first seal ring 104 and the second seal ring 105 are installed in the assembly cavity, the axial thickness of the output shaft 204 is compressed to 70%, so that the sealing performance between the flange seat 101 and the flange cover 106 can be better sealed, and oil leakage can be prevented.

In one embodiment, the first seal ring 104 and the second seal ring 105 have a height difference in the height direction.

In the present embodiment, the first seal ring 104 and the second seal ring 105 are provided at different heights in the height direction or in the extending direction of the output shaft 204, and are not flush with each other.

When the flange base 101 and the flange cover 106 are in interference fit, the flange base 101 and the flange cover 106 form an interference fit with each other for both the inner ring wall and the outer ring wall of the annular body. If the first sealing ring 104 and the second sealing ring 105 are located at the same height position, the inner wall and the outer wall of the flange cover 106 may be pressed toward the same direction, and at this time, it is not necessary to ensure that the inner wall and the outer wall of the flange cover 106 both apply an acting force to the first sealing ring 104 and the second sealing ring 105, which is not beneficial to ensure that the first sealing ring 104 and the second sealing ring 105 achieve a good sealing effect at the same time.

Forces applied to both the inner and outer sides of the seal ring tend to deform the cross-sectional cavity of the raceway 107. If the first seal ring 104 and the second seal ring 105 are at the same height, the cavity cross-sectional deformation of the raceway 107 tends to be biased to one side along the axial direction, which affects the sealing effect. On the contrary, when the first seal ring 104 and the second seal ring 105 are not at the same height, it is beneficial to ensure that the cross section of the cavity of the raceway 107 is deformed and stressed, thereby being beneficial to ensure the sealing effect.

In a specific embodiment, as shown in fig. 11, the outer edge of the flange cover 106 is provided with a first fitting part 1062, and the outer edge of the flange seat 101 is provided with a second fitting part 1013. The first engagement portion 1062 and the second engagement portion 1013 are engaged with each other to form a caulking structure. Specifically, the riveting structure may be a positive riveting structure or a reverse riveting structure.

In one embodiment, the flange seat 101 has an inner ring portion 1063 and an outer ring portion 1064 opposite to each other, and a contact height of the inner ring portion 1063 and the flange cover 106 in an axial direction of the output shaft 204 is greater than a contact height of the outer ring portion 1064 and the flange cover 106, and an interference formed by the inner ring portion 1063 and the flange cover 106 is greater than an interference formed by the outer ring portion 1064 and the flange cover 106.

Specifically, along the axial direction of the output shaft 204, the contact height between the inner ring portion 1063 and the flange cover 106 is greater than the contact height between the outer ring portion 1064 and the flange cover 106, and the interference formed by the flange seat inner ring portion 1063 in cooperation with the flange cover 106 is greater than the interference formed by the outer ring portion 1064 and the flange cover 106, at this time, the second sealing ring 105 located on the inner side may be used to perform more sealing functions, so that the entire raceway 107 can be ensured to be deformed reasonably, and a good sealing effect is achieved.

It should be noted that, in the description of the present application, the terms "first", "second", and the like are used for descriptive purposes only and for distinguishing similar objects, and no precedence between the two is intended or should be construed to indicate or imply relative importance. In addition, in the description of the present application, "a plurality" means two or more unless otherwise specified.

The above embodiments in the present specification are all described in a progressive manner, and the same and similar parts among the embodiments may be referred to each other, and each embodiment is described with emphasis on being different from other embodiments.

The above description is only a few embodiments of the present invention, and although the embodiments of the present invention are described above, the above description is only for the convenience of understanding the present invention, and is not intended to limit the present invention. It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims

1. The utility model provides a clamp plate flange has the cyclic annular body that has the through-hole, this physical stamina of cyclic annular is installed on the output shaft through detachable shaft hole complex mode, its characterized in that, cyclic annular body includes: the flange cover and the flange seat are installed in a matched mode, the flange seat and the flange cover are matched to form a closed annular rolling way, and a rolling ball is arranged in the annular rolling way.

2. The platen flange of claim 1, having a centering mechanism disposed in the through-hole, the centering mechanism capable of ensuring that the platen flange rotates about the axis of the output shaft when the platen flange is coupled to the output shaft.

3. The platen flange of claim 2, wherein the centering mechanism comprises: the shaft centering element is arranged in the through hole and can elastically deform in the radial direction, and the outer side of the shaft centering element is abutted against the side wall of the through hole.

4. The platen flange of claim 3, wherein the centering element is a generally annular elastomer having an inner annular surface and an outer annular surface, the inner annular surface concentric with the outer annular surface.

5. The platen flange of claim 3, wherein the centering element is a metal spring plate having a telescoping portion disposed thereon, the telescoping portion having opposite outer tips that abut the sidewalls of the through-hole.

6. The platen flange of claim 3, wherein the centering element has opposite upper and lower end faces, and a height of the centering element from the upper end face to the lower end face is less than a height of the through hole along the rotational axis direction.

7. The platen flange of claim 1, wherein the balls are disposed in the raceway in a clearance fit with a lateral clearance therebetween;

The flange cover is provided with a first groove used for being matched with the rolling ball, at least the middle part of the cross section of the first groove is provided with an arc section, the circle center corresponding to the arc section projects to the horizontal plane where the center of the rolling ball is located, and the distance between the circle center and the center of the rolling ball is within the range of the lateral clearance.

8. The platen flange of claim 7, wherein a cross-section of the first groove comprises: the arc section is arranged in the middle, the trimming edges are arranged at two sides of the arc section and are in tangential transition with the arc section,

The flange seat is provided with a second groove matched with the rolling ball, the cross section of the second groove is a rectangle with rounded corners, and two sides of the rectangle are coplanar with the extension line of the trimming edge.

9. The platen flange of claim 7, wherein the arc of the circular arc segment is greater than 60 degrees.

10. The platen flange of claim 1 wherein the number of balls is an even number.

11. The platen flange of claim 10, wherein the number of balls is 6.

12. The platen flange of claim 1, wherein the flange seat and the flange cover are in interference fit, and a first sealing ring and a second sealing ring are respectively disposed at the positions where the flange seat and the flange cover are engaged,

The flange seat and the flange cover are matched to form an assembly cavity for mounting the first sealing ring and the second sealing ring; the size of the assembly cavity in a direction along the output shaft is no greater than the thickness of the first and second seal rings.

13. The platen flange of claim 12, wherein the first and second seal rings are compressed to 70% along the axial thickness of the output shaft after installation into the assembly cavity.

14. The platen flange of claim 12, wherein the first seal ring and the second seal ring have a height difference along a height direction.

15. The platen flange of claim 12, wherein an outer edge of the flange cover is provided with a first mating portion, an outer edge of the flange seat is provided with a second mating portion, and the first mating portion and the second mating portion are engaged to form a rivet structure.

16. The platen flange according to claim 1, wherein the flange seat has an inner ring portion and an outer ring portion that are opposed to each other, a contact height of the inner ring portion with the flange cover in an axial direction of the output shaft is larger than a contact height of the outer ring portion with the flange cover, and an interference formed by the inner ring portion for cooperation with the flange cover is larger than an interference formed by the outer ring portion with the flange cover.

17. An angle grinder having an output shaft and at least two platen flanges, wherein the output shaft is removably mounted alternatively to the at least two platen flanges and is capable of driving the platen flanges in coaxial rotation, and wherein the at least two platen flanges comprise a platen flange according to any one of claims 1 to 16.

18. The angle grinder of claim 17, wherein the at least two platen flanges further comprise a first platen flange having only a unitary annular body.

19. The angle grinder of claim 17, wherein a connecting portion is provided on a side wall of the through hole, and a first mounting portion matched with the connecting portion is provided on the output shaft, and the connecting portion and the first mounting portion cooperate to form a transmission structure for transmitting torque.

20. The angle grinder of claim 19, wherein an annular cavity is formed between the side wall of the output shaft and the side wall of the through hole, the centering mechanism comprising: the inner side of the centering shaft element is abutted against the side wall of the output shaft, and the outer side of the centering shaft element is abutted against the side wall of the through hole.

21. The angle grinder of claim 19, wherein the side wall of the output shaft is provided with an outer conical surface having a predetermined taper angle, the side wall of the through hole is provided with an inner conical surface having the same taper angle as the outer conical surface, and the outer conical surface and the inner conical surface are matched and fit to form the centering mechanism.

22. The angle grinder of claim 21, wherein the taper angle of the external taper or the internal taper is greater than 10 degrees.