CN107022875B - Washing machine speed reduction clutch - Google Patents
Washing machine speed reduction clutch Download PDFInfo
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- CN107022875B CN107022875B CN201610074230.1A CN201610074230A CN107022875B CN 107022875 B CN107022875 B CN 107022875B CN 201610074230 A CN201610074230 A CN 201610074230A CN 107022875 B CN107022875 B CN 107022875B
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- brake wheel
- spline
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- edge
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- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F37/00—Details specific to washing machines covered by groups D06F21/00 - D06F25/00
- D06F37/30—Driving arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
- F16D67/02—Clutch-brake combinations
Abstract
The invention relates to a washing machine speed reduction clutch, which comprises a brake wheel and a gear train arranged in the inner cavity of the brake wheel, wherein the brake wheel is provided with a small port and a large port, the small port is fixedly connected with a hollow dehydration shaft, a brake wheel cover is fixedly arranged on the large port, the gear train is a planetary gear train and is provided with an outer gear ring, and a plurality of outer splines are uniformly distributed on the outer circumferential surface of the outer gear ring; the inner cavity of the brake wheel is provided with a circle of internal splines matched with the external splines, and the external gear ring and the brake wheel are matched with each other through the external splines and the internal splines to realize coaxial rotation. The invention effectively enhances the connection strength of the brake wheel and the outer gear ring, improves the transmission torque and the matching centering property, prolongs the service life of the gear train, and ensures uniform torque distribution, small stress concentration and stable operation.
Description
Technical Field
The invention relates to the field of clutches, in particular to a decelerating clutch of a washing machine.
Background
The planetary gear train is a speed reducing mechanism of a speed reducing clutch of the washing machine, the planetary gear train is assembled in the brake wheel, an inner gear ring and an outer gear ring on the planetary gear train are fixed with the brake wheel, the brake wheel is held by the brake belt and does not move during washing, the input shaft transmits torque to the output shaft after being decelerated by the planetary gear train, and during dehydration, the brake belt is loosened, and the brake wheel and the planetary gear train rotate at high speed as a whole to realize dehydration. The existing washing machine speed reduction clutch mostly adopts the steps of processing a pin shaft on a brake wheel cover fixedly connected with a brake wheel and then connecting the pin shaft with pin holes on an inner gear ring and an outer gear ring so as to fix a planetary gear train, but the pin shaft positioning connection mode has insufficient connection strength and low matching precision.
The present invention has been made in view of this point.
Disclosure of Invention
The invention aims to provide a washing machine speed reduction clutch which has the advantages of high connection strength between a brake wheel and inner and outer gear rings, large transmission torque, uniform torque distribution and good centering property.
In order to realize the purpose, the invention adopts the following technical scheme:
a washing machine deceleration clutch comprises a brake wheel with a cylindrical inner cavity and a gear train arranged in the inner cavity of the brake wheel, wherein the brake wheel is provided with a small port and a large port, the small port is fixedly connected with a hollow dehydration shaft, the large port is provided with a brake wheel cover, the gear train is provided with an outer gear ring, and outer splines are uniformly distributed on the outer circumferential surface of the outer gear ring; the inner cavity of the brake wheel is provided with a circle of internal splines, and the external splines and the internal splines are mutually matched to enable the external gear ring and the brake wheel to coaxially rotate; the inner side of the large port of the brake wheel is also provided with a circle of inner end faces perpendicular to the axis of the brake wheel, the distance between each inner end face and the corresponding large port end face is not smaller than the thickness of the brake wheel cover, the maximum edge diameter of each inner end face is not smaller than the diameter of the tooth root circle of the inner spline, the distance between each inner end face and one end, far away from the large port, of the inner spline is larger than the axial length of the outer spline, and the brake wheel cover is arranged on each inner end face.
Furthermore, the internal spline is provided with a plurality of groove portions and a plurality of spline teeth connected with the groove portions, the peripheral wall of the inner cavity of the brake wheel, which is far away from the large port, is provided with a protruding portion corresponding to the groove portions, the protruding portion is connected with the end portions of the groove portions, the height of the protruding portion is not lower than the tooth top height of the spline teeth, and the length of the internal spline is slightly larger than that of the external spline matched with the internal spline.
Furthermore, both sides of the tooth top of the spline tooth are bulged upwards to form an inward concave tooth top surface with high both sides and low middle, and the bulges formed on both sides of the tooth top surface are inwards extended to be connected with the convex part along the edge of the tooth top surface from one end of the spline tooth close to the large port.
Furthermore, the bulges are ridge-shaped bulges, two ridge-shaped bulges which are close to the same groove part on two adjacent spline teeth are connected with the bulge part to form a U-shaped structure, and the bulge part is the bottom of the U-shaped structure and is crescent or semicircular; or the two sides of the tooth top of the spline tooth are upwards raised to form platform-shaped bulges, the top surface of each platform-shaped bulge is a plane, an inward concave shape is arranged between the two platform-shaped bulges on the tooth top of the spline tooth, and the width of the top surface of each platform-shaped bulge is larger than or equal to the width of the inward concave shape.
Further, the end, close to the big port, of the spline tooth of the internal spline is obliquely arranged to form a guide surface, so that the gear train can smoothly slide into the brake wheel, the opening end part of the U-shaped structure is inwards converged along the edge of the guide surface to form an internal splayed shape, and two ridge-shaped bulges on one tooth top surface are in a regular splayed shape at the end close to the big port and are gradually parallel in the direction away from the big port.
Further, the uplift is a platform-shaped bulge, the top surface of the platform-shaped bulge is a plane, two platform-shaped bulges on two adjacent spline teeth, which are close to the same groove portion, are connected with the bulge to form a U-shaped structure, the bulge is the bottom of the U-shaped structure and is crescent or semicircular, and the width of the platform-shaped bulge is not less than one third of the width of the tooth top surface.
Further, the inner spline is connected with the inner end face, the inner end face is provided with an outer edge and an inner edge, the outer edge is connected with the inner wall of the brake wheel, the diameter of the outer edge is larger than the diameter of a tooth root circle of the inner spline, the inner edge is connected with the tooth crest and the tooth root of the inner spline, the shape of the inner edge is the same as the shape of a tooth profile of the section of the inner spline, and a chamfer is further arranged at the joint of the inner end face and the tooth crest of the spline.
Furthermore, a space is reserved between the inner end surface of the inner cavity of the brake wheel and the end part of the internal spline, the inner end surface is connected with the inner wall of the brake wheel, and the diameter of the smallest edge of the inner end surface is larger than the diameter of the root circle of the internal spline; the end part of the internal spline, which is close to the large port, is provided with an internal spline end face, and the internal spline end face is provided with a concave-convex edge corresponding to the tooth form of the internal spline.
Further, the internal spline has a plurality of groove portions and a plurality of spline teeth connected thereto, the groove portions having: two side surfaces extending inwards from the large port of the brake wheel along the axis; the positioning surface is positioned at the end part of the groove part, which is far away from the open hole, of the groove part and is connected with the two side surfaces so as to realize the axial positioning of the gear train; the locating surface is arranged in an inclined mode and is connected with the bottom of the groove portion in a smooth mode, the outer spline of the outer gear ring and the end face matched with the locating surface are straight faces perpendicular to the axis of the outer gear ring, the two sides of the tooth top of the spline teeth are upwards bulged to form concave tooth top faces with high two sides and low middle, and the bulges formed on the two sides of the tooth top face are formed by the spline teeth close to one end of the large port and inwards extend to one end of the locating surface of the groove portion along the edge of the tooth top face.
Furthermore, the edge of one end, matched with the inner end face of the brake wheel, of the brake wheel cover is thinned to form an annular concave matching face, the matching face is attached to the inner end face of the brake wheel, the outer circular face of the brake wheel cover is in clearance fit with the inner wall of the large port of the brake wheel, the edge of the large port of the brake wheel is folded inwards and pressed on the brake wheel cover, and the brake wheel is fixedly connected with the brake wheel cover.
After the technical scheme of the invention is adopted, the following beneficial effects are brought:
the brake wheel and the planetary gear train of the washing machine speed reduction clutch are matched through the plurality of internal splines and the plurality of external splines arranged on the matching surface to form the spline matching of mutual meshing, so that the connection strength can be effectively enhanced, the centering performance of the transmission torque and the matching is improved, and the gear train is allowed to axially move slightly in the brake wheel, so that the pressure borne by the gear train in the vibration process or the overheating expansion process can be released, the service life of the gear train is prolonged, the torque distribution is uniform, the stress concentration is small, and the operation is stable.
Drawings
FIG. 1 is an assembly schematic of the present invention;
FIG. 2 is a structural cross-sectional view of the brake wheel according to the first embodiment of the present invention;
FIG. 3 is an enlarged partial schematic view of I of FIG. 2;
FIG. 4 is a left side view of the headblock in a first embodiment of the present invention;
FIG. 5 is an enlarged partial schematic view of II of FIG. 4;
FIG. 6 is a structural cross-sectional view of the outer ring gear of the present invention;
FIG. 7 is a left side elevational view of the outer ring gear of the present invention;
FIG. 8 is a structural sectional view of the brake wheel in the second embodiment of the present invention;
FIG. 9 is a left side view of the headblock in accordance with embodiment two of the present invention;
FIG. 10 is an enlarged partial schematic view of I of FIG. 8;
FIG. 11 is an enlarged partial schematic view of II of FIG. 9;
FIG. 12 is a structural cross-sectional view of the brake wheel cover of the present invention;
the reference numbers in the figures are: 1-input shaft 2-gear train 3-external gear ring 4-planet wheel 5-brake wheel 6-internal spline 7-positioning surface 8-guide surface 9-two side surfaces 10-internal end surface 11-flanging 12-brake wheel cover 13-dewatering shaft 14-planet wheel fixing frame 31-external spline 51-large port 52-small port 61-groove part 62-spline tooth 63-bottom surface 64 of groove part-tooth top surface 65-ridge protrusion 66-protrusion part 67-internal spline end surface 68-platform protrusion 121-shaft hole 122-matching surface.
Detailed Description
The following describes embodiments of the present invention in further detail with reference to the accompanying drawings.
As shown in fig. 1, a decelerating clutch of a washing machine includes a brake wheel 5 having a cylindrical inner cavity, a gear train 2 installed in the inner cavity of the brake wheel 5, wherein one end of the brake wheel 5 is large in size and is opened to form a large port 51 for fitting the gear train 2; the other end is contracted along the radial direction to form a funnel shape and is a small port 52, the small port 52 is fixedly connected with a hollow dehydration shaft 13, and the dehydration shaft 13 rotates together with the brake wheel 5. A brake wheel cover 12 is fixedly arranged at the large port 51, the brake wheel cover 12 is provided with an outer circular surface matched with the large port 51 in size and a shaft hole 121 penetrating through the center of the brake wheel cover 12, the brake wheel cover 12 limits the gear train 2 in an inner cavity of the brake wheel 5, the gear train 2 is a planetary gear train and is provided with an outer gear ring 3, a planetary gear 4 meshed with the outer gear ring 3 and a planetary gear fixing frame 14 for fixing the planetary gear 4, an input shaft 1 is arranged at the center of the planetary gear 4, the input shaft 1 is meshed with the planetary gear 4, and one end of the input shaft penetrates through the shaft hole 121 of the brake wheel cover 12 to be connected with a motor shaft so as to transmit motor.
Referring to fig. 2, 6 and 7, a plurality of external splines 31 are arranged on the outer circumferential surface of the external gear ring 3, a circle of internal splines 6 which are uniformly distributed is arranged on the inner cavity wall of the brake wheel 5, the internal splines 6 are arranged at a distance from the end surface of the large port 52, the distance is greater than the thickness of the brake wheel cover 12, the external splines 31 on the external gear ring 3 are engaged with the internal splines 6 of the brake wheel 5, so that the external gear ring 3 and the brake wheel 5 rotate coaxially, preferably, the length of the internal splines 6 is slightly greater than that of the external splines 31 which are matched with the internal splines 6, and specifically, the length of the internal splines 6 may be 2-5mm longer than that of the external splines.
Example one
As shown in fig. 3, a ring of inner end surface 10 perpendicular to the axis of the brake wheel 5 is further disposed on the inner side of the large port 51 of the brake wheel 5, the distance between the inner end surface 10 and the large port 51 is not less than the thickness of the brake wheel cover 12, the diameter of the inner cavity of the brake wheel 5 is changed on the inner end surface 10, specifically, the inner end surface 10 is used as a boundary line, the diameter of the inner cavity of the brake wheel 5 on the side close to the large port 51 is greater than the diameter of the inner cavity on the side away from the large port 51, the maximum edge diameter of the inner end surface 10 is not less than the diameter of the root circle of the internal spline 6, the brake wheel cover 12 is disposed on the inner end surface 10, and the inner end surface 10 plays a. Preferably, the distance between the inner end surface 10 and the end of the internal spline 6 far away from the large port 51 is greater than the axial length of the external spline 31, so that the brake wheel cover 12 does not generate extrusion force on the external gear ring 3, and after the brake wheel cover 12 is connected with the brake wheel 5, the external gear ring 3 can axially move slightly in the brake wheel 5, thereby ensuring uniform stress on the external gear ring 3 and reducing noise generated during operation of the gear train 2.
Specifically, a distance is formed between an inner end surface 10 of an inner cavity of the brake wheel 5 and the end part of the internal spline 6, the distance is preferably 1-3mm in size, one side edge of the inner end surface 10 is connected with the inner wall of the brake wheel 5, and the diameter of the smallest edge of the inner end surface is larger than the diameter of a root circle of the internal spline 6.
As shown in fig. 12, an end of the brake wheel cover 12, which is matched with the inner end surface 10 of the inner cavity of the brake wheel 5, is thinned at an edge to form an annular concave matching surface 122, the matching surface 122 is attached to the inner end surface 10, the outer circular surface of the brake wheel cover 12 is in clearance fit with the inner wall of the large port 51 of the brake wheel 5, and the edge of the large port 51 of the brake wheel 5 is turned inwards and pressed on the brake wheel cover 12, so that the brake wheel 5 and the brake wheel cover 12 form a fixed connection.
As shown in fig. 4 and 5, the internal spline 6 has a plurality of groove portions 61 and a plurality of spline teeth 62 connected thereto, and the groove portions 61 have: the brake wheel comprises two side surfaces 9, a positioning surface 7 and a bottom surface 63 of a groove part, wherein the two side surfaces 9 extend inwards from one end of a large port 51 along the axial direction, the extending distance of the two side surfaces is matched with the length of an external spline 31 of an external gear ring 3, the two side surfaces 9 are matched with the external spline 31 of the external gear ring 3 to transmit the acting force of coaxial rotation, the distance between the two side surfaces 9 of the groove part 61 is gradually increased from the bottom surface 63 of the groove part to the axial direction of the brake wheel 5, and the section shape of the groove part 61. The positioning surface 7 is positioned at one end of the groove part 61 far away from the large port 51 and is connected with two side surfaces 9, and the positioning surface 7 is matched with one end surface of the external spline 31 to realize axial positioning of the gear train 2; specifically, the two side surfaces 9 of the groove portion 61 are in clearance fit with the external spline 31, so that the external gear ring 3 can be smoothly installed in the brake wheel 5, and the positioning surface 7 is in contact with one end surface of the external spline 31, so that the external gear ring 3 can be axially positioned and supported by the positioning surface 7 when the brake wheel 5 is installed.
The positioning surface 7 is smoothly connected with the bottom of the groove portion 61, and forms an acute angle with the bottom surface 63 of the groove portion, and preferably, an included angle alpha between the positioning surface 7 and the bottom surface 63 of the groove portion is 45 degrees; the end face of the external spline 31 matched with the positioning face 7 is a straight face perpendicular to the axis of the external gear ring 3, and when the external spline 31 is installed, the straight face at one end of the external spline 31 is contacted with the part, close to the bottom of the internal spline 6, of the positioning face 7, so that positioning is achieved.
Preferably, the inner cavity wall of the brake wheel 5 is provided with protruding portions 66 at intervals corresponding to the groove portions 61, the protruding portions 66 are located at one end of the groove portions 61 far away from the large port 51 and connected with the end portions of the groove portions 61, and the height of the protruding portions 66 is not lower than the tooth crest height of the spline teeth 62. Specifically, the protruding portion 66 is connected to the positioning surface 7 and extends to the rear side of the internal spline 6 along the positioning surface 7, the area of the positioning surface 7 is increased by the arrangement of the protruding portion 66, the strength of the internal spline 6 at this position is improved, and the protruding portion 66 is formed by a cold extrusion process.
Preferably, both sides of the tooth top of the spline tooth 62 are raised upwards to form a concave tooth top 64 with two high sides and a low middle part, the two sides of the tooth top 64 are formed with a ridge extending inwards from one end of the spline tooth 62 close to the large port 51 along the edge of the tooth top 64 to be connected with the convex part 66, and the two sides of the tooth top of the spline tooth 62 are raised upwards to improve the strength of the internal spline 6.
Specifically, the ridge-shaped protrusion 65 is formed by connecting two ridge-shaped protrusions 65 and protruding parts 66, which are close to the same groove part 61, on two adjacent spline teeth 62 to form a U-shaped structure surrounding the edge of the groove part 61, the protruding parts 66 are the bottom of the U-shaped structure and are crescent or semicircular, and the ridge-shaped protrusion 65 is formed by a cold extrusion process.
The end of the spline teeth 62 of the internal spline 6 near the large port 51 is obliquely arranged to form a guide surface 8, the guide surface 8 is connected with the tooth crest 64 of the spline teeth 62 to enable the gear train 2 to smoothly slide into the brake wheel 5, the guide surface 8 extends obliquely inward in the axial direction from the side near the inner end surface 10, and the included angle c between the guide surface 8 and the bottom surface 63 of the groove portion is 15 °, but it should be understood by those skilled in the art that the angle is only one embodiment of the present invention, but is not limited to this, and may be 20 °, 30 or any other angle not exceeding 90 °.
As shown in fig. 3, the end of the internal spline 6 near the large port 51 is preferably provided with an internal spline end surface 67, the internal spline end surface 67 has a concave-convex edge corresponding to the tooth shape of the internal spline 6, and the internal spline end surface 67 is connected with the inner wall of the brake wheel 5 on one side and the guide surface 8 at the spline teeth 62 on the other side.
The open end of the U-shaped structure converges inwardly along the edge of the guide surface 8 to form an inner splaying and the two ridges 65 on one tooth crest 64 are regular splayed at the end near the large port 51 and are progressively parallel in the direction away from the large port 51.
Preferably, the depth of the teeth of the internal spline 6 is controlled to 0.8mm in order not to reduce the strength of the brake wheel 5 and to ensure the convenience of assembling the gear train 2, while the number of teeth of the internal spline 6 is designed to be 36 in order to ensure the connection strength of the traveling gear train 2 and the brake wheel 5 in the circumferential direction.
As shown in fig. 3, the edge of the large port 51 of the brake wheel 5 is thinned to form a foldable flange 11, and the flange 11 is bent towards the inner cavity of the brake wheel 5 after the brake wheel cover 12 is installed in the brake wheel 5 through rolling treatment and is tightly pressed and wrapped on the outer side of the brake wheel cover 12, so that the brake wheel cover 12 and the brake wheel 5 form a fixed connection. The turned edge 11 can be formed by turning the outer circumferential surface of the large port 51 of the brake wheel 5 to make the thickness of the turned edge smaller than the wall thickness of the brake wheel 5, so as to facilitate rolling processing.
Example two
The difference between this embodiment and the first embodiment is:
referring to fig. 9 and 11, the protrusion of the present embodiment is a flat protrusion 68, the top surface of the flat protrusion 68 is a flat surface, an inward concave shape is formed between two flat protrusions 68 on the tooth top surface 64 of the spline tooth 62, the width of the top surface of the flat protrusion 68 is greater than or equal to the width of the inward concave shape, two flat protrusions 68 on two adjacent spline teeth 62 close to the same groove 61 are connected with the protrusion 66 to form a U-shaped structure, the protrusion 66 is the bottom of the U-shaped structure and is crescent or semicircular, the U-shaped structure surrounds the edge of the groove 61 and is formed by a cold extrusion process, and preferably, the width of the flat protrusion 68 is not less than one third of the width of the tooth top surface 64.
Referring to fig. 8 and 10, in this embodiment, the inner end surface 10 is directly connected to the internal spline 6 and serves as an end surface of the internal spline 6 near one side of the large port, the inner end surface 10 has an outer edge and an inner edge, the outer edge is connected to the inner wall of the brake wheel 5, the diameter of the outer edge is larger than the diameter of the tooth root circle of the internal spline 6, the inner edge is connected to the tooth crest and the tooth root of the internal spline 6, the shape of the inner edge is the same as the shape of the tooth profile of the cross section of the internal spline 6, and a chamfer is further provided at the connection position of the inner end surface 10 and the tooth crest of the internal spline 6, so that the gear.
The installation method of the invention comprises the following steps: after the gear train 2 is assembled, the gear train is installed into the brake wheel 5 from the large port 51, the external spline 31 of the external gear ring 3 is meshed with the internal spline 6 of the brake wheel 5 to form spline connection, after the external spline 31 of the external gear ring 3 is contacted with the positioning surface 7, axial positioning is achieved, then the brake wheel cover 12 is installed, the outer circular surface of the brake wheel cover 12 is in clearance fit with the inner wall of the brake wheel 5 to facilitate installation of the brake wheel cover 12, the end surface of the brake wheel cover 12 is contacted with the inner end surface 10 to achieve axial positioning, the flanging 11 of the brake wheel 5 is rolled to be turned over to be contacted with the brake wheel cover 12, and the brake wheel cover 12 is pressed tightly, so that assembly is completed.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, many variations and modifications can be made without departing from the principle of the present invention, which should also be regarded as the protection scope of the present invention.
Claims (10)
1. A decelerating clutch of a washing machine comprises a brake wheel with a cylindrical inner cavity, and a gear train arranged in the inner cavity of the brake wheel, wherein the brake wheel is provided with a small port and a big port, the small port is fixedly connected with a hollow dewatering shaft, and a brake wheel cover is arranged on the big port, and the decelerating clutch is characterized in that: the gear train is provided with an outer gear ring, and outer splines are uniformly distributed on the outer circular surface of the outer gear ring; the inner cavity of the brake wheel is provided with a circle of internal splines, and the external splines and the internal splines are mutually matched to enable the external gear ring and the brake wheel to coaxially rotate; the inner side of the large port of the brake wheel is also provided with a circle of inner end faces perpendicular to the axis of the brake wheel, the distance between each inner end face and the corresponding large port end face is not smaller than the thickness of the brake wheel cover, the maximum edge diameter of each inner end face is not smaller than the diameter of the tooth root circle of the inner spline, the distance between each inner end face and one end, far away from the large port, of the inner spline is larger than the axial length of the outer spline, and the brake wheel cover is arranged on each inner end face.
2. The decelerating clutch of a washing machine as claimed in claim 1, wherein: the inner spline is provided with a plurality of groove portions and a plurality of spline teeth connected with the groove portions, the peripheral wall of the inner cavity of the brake wheel, which is far away from the large port, is provided with a protruding portion corresponding to the groove portions, the protruding portion is connected with the end portions of the groove portions, the height of the protruding portion is not lower than the height of tooth tops of the spline teeth, and the length of the inner spline is slightly larger than that of an outer spline matched with the inner spline.
3. The decelerating clutch of a washing machine as claimed in claim 2, wherein: the two sides of the tooth top of the spline tooth are bulged upwards to form an inward concave tooth top surface with two high sides and a low middle part, and the bulges formed on the two sides of the tooth top surface are inwards extended to be connected with the convex part along the edge of the tooth top surface from one end, close to the large port, of the spline tooth.
4. A washing machine decelerating clutch according to claim 3, characterised in that: the ridge-shaped bulges are connected with the protruding parts to form a U-shaped structure, and the protruding parts are the bottoms of the U-shaped structures and are crescent or semicircular; or the two sides of the tooth top of the spline tooth are upwards raised to form platform-shaped bulges, the top surface of each platform-shaped bulge is a plane, an inward concave shape is arranged between the two platform-shaped bulges on the tooth top of the spline tooth, and the width of the top surface of each platform-shaped bulge is larger than or equal to the width of the inward concave shape.
5. The decelerating clutch of a washing machine as claimed in claim 4, wherein: the end, close to the big port, of the spline tooth of the internal spline is obliquely arranged to form a guide surface so that the gear train can smoothly slide into the brake wheel, the opening end part of the U-shaped structure inwards converges along the edge of the guide surface to form an inner splayed shape, and two ridge-shaped bulges on one tooth top surface are in a regular splayed shape at the end close to the big port and are gradually parallel along the direction far away from the big port.
6. A washing machine decelerating clutch according to claim 3, characterised in that: the uplift is platform-shaped protrusion, the top surface of the platform-shaped protrusion is a plane, two platform-shaped protrusions close to the same groove portion on two adjacent spline teeth are connected with the protruding portion to form a U-shaped structure, the protruding portion is the bottom of the U-shaped structure and is crescent or semicircular, and the width of the platform-shaped protrusion is not less than one third of the width of the tooth top surface.
7. The decelerating clutch of a washing machine as claimed in claim 1 or 6, wherein: the inner spline is connected with the inner end face, the inner end face is provided with an outer edge and an inner edge, the outer edge is connected with the inner wall of the brake wheel, the diameter of the outer edge is larger than the diameter of a tooth root circle of the inner spline, the inner edge is connected with the tooth top and the tooth root of the inner spline, the shape of the inner edge is the same as the tooth profile shape of the section of the inner spline, and a chamfer is further arranged at the joint of the inner end face and the tooth top of the spline.
8. The decelerating clutch of a washing machine as claimed in claim 1 or 5, wherein: a space is reserved between the inner end surface of the inner cavity of the brake wheel and the end part of the internal spline, the inner end surface is connected with the inner wall of the brake wheel, and the diameter of the minimum edge of the inner end surface is larger than the diameter of the root circle of the internal spline; the end part of the internal spline, which is close to the large port, is provided with an internal spline end face, and the internal spline end face is provided with a concave-convex edge corresponding to the tooth form of the internal spline.
9. The decelerating clutch of a washing machine as claimed in claim 1, wherein: the internal spline has a plurality of groove portions and a plurality of spline teeth connected thereto, the groove portions having: two side surfaces extending inwards from the large port of the brake wheel along the axis; the positioning surface is positioned at the end part of the groove part, which is far away from the open hole, of the groove part and is connected with the two side surfaces so as to realize the axial positioning of the gear train; the locating surface is arranged in an inclined mode and is connected with the bottom of the groove portion in a smooth mode, the outer spline of the outer gear ring and the end face matched with the locating surface are straight faces perpendicular to the axis of the outer gear ring, the two sides of the tooth top of the spline teeth are upwards bulged to form concave tooth top faces with high two sides and low middle, and the bulges formed on the two sides of the tooth top face are formed by the spline teeth close to one end of the large port and inwards extend to one end of the locating surface of the groove portion along the edge of the tooth top face.
10. The decelerating clutch of a washing machine as claimed in claim 1, wherein: the edge of one end, matched with the inner end face of the brake wheel, of the brake wheel cover is thinned to form an annular concave matching face, the matching face is attached to the inner end face of the brake wheel, the outer circular face of the brake wheel cover is in clearance fit with the inner wall of the large port of the brake wheel, the edge of the large port of the brake wheel is turned inwards and pressed on the brake wheel cover, and the brake wheel is fixedly connected with the brake wheel cover.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610074230.1A CN107022875B (en) | 2016-02-01 | 2016-02-01 | Washing machine speed reduction clutch |
| PCT/CN2017/071906 WO2017133489A1 (en) | 2016-02-01 | 2017-01-20 | Brake disc of gear reduction clutch in washing machine and washing machine gear reduction clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610074230.1A CN107022875B (en) | 2016-02-01 | 2016-02-01 | Washing machine speed reduction clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107022875A CN107022875A (en) | 2017-08-08 |
| CN107022875B true CN107022875B (en) | 2020-06-19 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610074230.1A Active CN107022875B (en) | 2016-02-01 | 2016-02-01 | Washing machine speed reduction clutch |
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| Country | Link |
|---|---|
| CN (1) | CN107022875B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001204989A (en) * | 2000-01-28 | 2001-07-31 | Matsushita Electric Ind Co Ltd | Washing machine |
| CN102021790A (en) * | 2010-12-21 | 2011-04-20 | 海尔集团公司 | Transmission system for sports washing machine and washing machine |
| CN205382334U (en) * | 2016-02-01 | 2016-07-13 | 浙江三星机电股份有限公司 | Retarding clutch for washing machine |
-
2016
- 2016-02-01 CN CN201610074230.1A patent/CN107022875B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001204989A (en) * | 2000-01-28 | 2001-07-31 | Matsushita Electric Ind Co Ltd | Washing machine |
| CN102021790A (en) * | 2010-12-21 | 2011-04-20 | 海尔集团公司 | Transmission system for sports washing machine and washing machine |
| CN205382334U (en) * | 2016-02-01 | 2016-07-13 | 浙江三星机电股份有限公司 | Retarding clutch for washing machine |
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| CN107022875A (en) | 2017-08-08 |
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