Roller type bidirectional gear clutch

Abstract

The utility model provides a roller type bidirectional gear clutch. The end cover pressure spring gasket, the end cover pressure spring and the driving fluted disc are sequentially and coaxially arranged on a cylinder of the driven gear shaft, the two end covers are arranged on the two sides of the driving fluted disc, and the rollers are matched with roller reset pressure springs and are arranged in wedge-shaped track slotted holes of the driving fluted disc. Free separation and reunion switching in the forward rotation direction and the backward rotation direction between the driving fluted disc and the driven gear shaft which is coaxially connected with the driving fluted disc in a clearance fit mode can be achieved, the driven gear shaft, namely a torsion output transmission end mechanism, can be released from the driving fluted disc freely when a roller is disengaged, and free manual operation of the torsion output transmission end mechanism is achieved. The roller type bidirectional gear clutch is novel, simple, efficient, pure in mechanical structure and capable of being integrated manually and automatically, and the problems that various roller type clutches widely applied at present are relatively complex and tedious in structure, large in size, high in cost, inconvenient to operate, not ideal in efficiency and reliability and the like are solved.

Description

Technical Field

[0001] The utility model relates to the technical field of clutches, in particular to a roller type bidirectional gear clutch. Background Art

[0002] At present, various types of roller clutches are widely used in mechanical devices or equipment for torque transmission or output in the market. Among them, pure mechanical roller clutches are divided into manual and manual-automatic. Such manual roller clutches are inconvenient to use and require manual operation of the clutch. Manual-automatic roller clutches are usually relatively complex and cumbersome in structure, and their efficiency, cost, and reliability are not ideal. Electric, pneumatic, or hydraulic roller two-way clutches are relatively complex and cumbersome in size and structure, especially large in size, high in cost, and not ideal in efficiency and reliability. Therefore, such roller two-way gear clutches, whether they are pure mechanical, electric, pneumatic, or hydraulic, are not the best technical solutions in conventional applications. Utility Model Content

[0003] Therefore, the technical problem to be solved by the present invention is that the roller-type bidirectional gear clutch in the prior art is relatively complex and cumbersome in structure, and its efficiency, cost, reliability and other aspects are not ideal.

[0004] To this end, the utility model provides a roller type bidirectional gear clutch, comprising a driven gear shaft, an end cover compression spring gasket, an end cover compression spring, a driving gear plate assembly, two end covers arranged on both sides of the driving gear plate assembly and an axial retaining ring;

[0005] Among them, the end cover compression spring gasket, the end cover compression spring, the active gear plate assembly, two end covers arranged on both sides of the active gear plate assembly, and the axial retaining ring are connected in sequence with the shaft hole gap and coaxially arranged on the passive gear shaft cylinder.

[0006] Optionally, the upper end of the driven gear shaft is a toothed structure, the middle is a cylinder, and the end is provided with an axial retaining ring groove, and the retaining ring is arranged in the retaining ring groove.

[0007] Optionally, the active toothed disc assembly is composed of one or more pairs of rollers and roller return compression springs arranged in one or more pairs of wedge-shaped track slots of the active toothed disc;

[0008] The outer ring of the active gear disc is a toothed structure, with a discontinuous cylindrical hole in the center. The cylindrical hole wall is distributed outward with at least one or more pairs of semi-open track slots that are arranged relatively on the circumference and in opposite directions in the radial direction, forming a straight wedge-shaped or arc-shaped wedge-shaped track slot on the outer side with the inner cylindrical surface.

[0009] Optionally, the height value H of the two end surfaces of the roller is greater than the thickness h of the active gear plate, and one or more pairs of rollers are arranged together with roller return springs in the wedge-shaped track slots formed after the active gear plate and the passive gear shaft are coaxially mounted with a clearance, and their axes are parallel to the axes of the latter two.

[0010] Optionally, both ends of the roller return compression spring respectively press against the side wall of the wedge-shaped track groove end of the active gear disk and the roller column surface to apply a radial pre-compression thrust to the roller so that the latter can always maintain a tendency to disengage from the wedging of the small head of the wedge-shaped track groove.

[0011] Optionally, two end covers are respectively arranged on both sides of the active gear plate assembly, pressed on both ends of the roller, and assembled together with the clearance fit of the cylindrical shaft hole of the passive gear shaft.

[0012] Optionally, the end cover compression spring is sleeved on the middle cylinder of the driven gear shaft, with one end pressing on the end cover compression spring gasket and the other end pressing on the adjacent end cover so that both ends of each roller are pressed between the two end covers with an appropriate pre-pressure and the friction force of each roller on the contact surface of the end cover is greater than the maximum thrust of the roller return compression spring on the roller.

[0013] Optionally, on the cross section of the active gear disc, there is at least one point on the continuous track surface projection line of the semi-open wedge-shaped track slot, and there is an angle β between the lateral perpendicular line passing through this point on the wedge surface and the line connecting this point and the center of the inner center circle, and the value range of the angle β can be an angle value within twice the friction dead angle.

[0014] The utility model provides a roller type bidirectional gear clutch, which has the following advantages:

[0015] The utility model provides a roller type two-way gear clutch, which consists of a passive gear shaft, an end cover compression spring gasket coaxially arranged on the cylindrical body of the passive gear shaft, an end cover compression spring, a driving toothed disc, two end covers arranged on both sides of the driving toothed disc, and a pair or more rollers equipped with roller reset compression springs arranged in the wedge-shaped track slot holes of the driving toothed disc. The utility model can realize the free clutch switching between the positive and negative rotation directions between the active toothed disc and the passive gear shaft connected by the clearance fit of the coaxial hole. When the roller is disengaged from the wedging, the passive gear shaft, that is, the torque output transmission end mechanism, can be released and free from the active toothed disc, thereby realizing the torque output transmission end mechanism that can be freely manually operated. The utility model is a novel, simple and efficient roller type two-way gear clutch with a pure mechanical structure that can be manually and automatically integrated, and solves the problems of relatively complex and cumbersome structures, large volumes, high costs, inconvenient operations, and unsatisfactory efficiency and reliability of various roller type clutches widely used in the current market. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the specific implementation methods of the utility model or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0017] Figure 1 This is an exploded isometric view of a roller-type bidirectional gear clutch of the utility model;

[0018] Figure 2 It is a partially cutaway axonometric view of a roller-type bidirectional gear clutch of the utility model;

[0019] Figure 3 It is a second view of the active gear disc of the utility model;

[0020] Figure 4 It is a second view of the active toothed disc assembly of the utility model;

[0021] Figure 5 It is an axonometric view of the passive gear shaft of the utility model.

[0022] Description of reference numerals:

[0023] 1- driving gear disc;

[0024] 2- driven gear shaft;

[0025] 3- Roller;

[0026] 4-Roller return compression spring;

[0027] 5-end cap;

[0028] 6-end cover compression spring gasket;

[0029] 7- axial retaining ring;

[0030] 8-End cover compression spring. DETAILED DESCRIPTION

[0031] The technical solution of the utility model will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0032] In the description of the present utility model, it should be noted that the terms "center", "up", "down", "left", "right", "vertical", "horizontal", "inside", "outside" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation on the present utility model. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance. In addition, the technical features involved in the different embodiments of the present utility model described below can be combined with each other as long as they do not conflict with each other.

[0033] Example 1

[0034] Figure 1 , Figure 2 It is an exploded isometric view and a partially cut-away isometric view of an embodiment of the utility model. In the figure, the utility model manual-automatic roller type two-way gear clutch is composed of a passive gear shaft 2, and an end cover compression spring gasket 6 coaxially arranged on the passive torque shaft cylinder, an end cover compression spring 8, a driving gear plate 1, two end covers 5 arranged on both sides of the driving gear plate 1, an axial retaining ring 7, and a pair or more of cylindrical rollers 3 equipped with roller return compression springs 4 and arranged in the wedge-shaped track slot of the driving gear plate 1; the upper end of the passive gear shaft 2 is a toothed structure, the middle is a cylinder, and the end has an axial retaining ring groove.

[0035] Figure 3 1 is a two-view drawing of the active gear disc 1 of the utility model. The outer ring of the active gear disc 1 is tooth-shaped, and the center of the inner ring is a discontinuous cylindrical hole. The cylindrical hole wall is distributed outward with at least one pair or more pairs of semi-open track slots that are arranged relatively on the circumference and in opposite directions in the radial direction, and form a straight wedge-shaped or arc-shaped wedge-shaped track slot with its inner cylindrical surface on the outer side. On the end view of the active gear disc 1, there is always at least one such point on the continuous track surface projection line of the semi-open wedge-shaped track slot, and the lateral perpendicular line passing through this point on the wedge surface and the line connecting this point and the inner center circle center have an angle β, and the value range of the angle β is an angle value within twice the friction dead angle.

[0036] Figure 4The utility model is a second view of the active toothed disc assembly, which is composed of one or more pairs of cylindrical rollers 3 and roller return compression springs 4 arranged together in one or more pairs of wedge-shaped track slots of the active toothed disc 1: when the rollers 3 are wedged in the structure, their cylindrical working surfaces are tangent to the wedge-shaped slot surface of the active toothed disc 1 and the cylindrical surface of the passive gear shaft 2, and the height value H of the two end surfaces is greater than the thickness value h of the active toothed disc 1; one or more pairs of rollers 3 and roller return compression springs 4 are arranged together in one or more pairs of wedge-shaped track slots of the active toothed disc 1, and their axes are parallel to the axes of the latter two, and the two ends of the roller return compression spring 4 are respectively pressed against the side walls of the wedge-shaped track slot ends of the active toothed disc 1 and the columnar surface of the rollers 3 to apply a radial pre-pressure thrust to the rollers 3 so that the latter can always maintain a tendency state that can be disengaged from the wedging with the wedge-shaped track slot.

[0037] Figure 5 It is an axial side view of the passive gear shaft 2 of the utility model. The upper end of the passive gear shaft 2 is a gear structure, the middle is a cylinder, and there is a ring groove for an axial retaining ring 7 near the end, which can be connected in the mechanism through its shaft hole.

[0038] Combined by Figure 1 , Figure 2 , Figure 3 ,to Figure 4 , Figure 5It can be seen that the roller-type bidirectional gear clutch of the utility model is composed of a passive gear shaft 2, an end cover compression spring gasket 6, an end cover compression spring 8, a driving toothed disc assembly, two end covers 5 arranged on both sides of the active toothed disc assembly, and an axial retaining ring 7: the end cover compression spring gasket 6, the end cover compression spring 8, the active toothed disc assembly, the two end covers 5 arranged on both sides of the active toothed disc assembly, and the axial retaining ring 7 are sequentially connected with the shaft hole gap and coaxially arranged on the cylinder of the passive gear shaft 2; the upper end of the passive gear shaft 2 is a toothed structure, the middle is a cylinder, and the end has an axial retaining ring groove; the active toothed disc assembly is composed of one or more pairs of rollers 3 and roller reset compression springs 4 arranged together in one or more pairs of wedge-shaped track slots of the active toothed disc 1. The outer ring of the active gear disc 1 is a toothed structure, with a discontinuous cylindrical hole in the center. The cylindrical hole wall is distributed outward with at least one or more pairs of semi-open track slots that are arranged relatively on the circumference and in opposite directions in the radial direction, and form a straight wedge-shaped or arc-shaped wedge-shaped track slot with its inner cylindrical surface on the outer side. On the end face view of the active gear disc 1, there is always at least one such point on the continuous track surface projection line of the semi-open wedge-shaped track slot, and the angle β between the lateral perpendicular line passing through this point on the wedge surface and the line connecting this point and the center of the inner circle can be within a value range of twice the angle of a friction dead angle, wherein the above-mentioned friction dead angle is the wedge angle between the built-in circle and the wedge-shaped track surface, and the built-in circle is the circle where the above-mentioned cylindrical hole is located. After the central cylindrical hole wall and the surface of the middle cylinder of the driven gear shaft 2 are assembled with a coaxial gap, at least one or more pairs of closed wedge-shaped track grooves are formed, which are arranged oppositely on the circumference and have straight or curved outer surfaces and cylindrical inner surfaces in opposite radial directions; the height value H of the two end surfaces of the roller 3 is greater than the thickness h value of the active gear plate 1, and one or more pairs of rollers 3 are arranged together with the roller return compression spring 4 in these wedge-shaped track groove holes formed after the active gear plate 1 and the driven gear shaft 2 are assembled with a coaxial gap, and the axis thereof is parallel to the axis of the latter two; the two ends of the roller return compression spring 4 are respectively pressed against the side wall of the wedge-shaped track groove end of the active gear plate 1 and the column surface of the roller 3 to apply a radial pre-pressure thrust to the roller 3 so that the latter can always maintain a position that can be disengaged from the wedging with the small head of the wedge-shaped track groove. Trend state; the two end covers 5 are respectively arranged on both sides of the active gear disc assembly, pressed on the two ends of the roller 3, and matched with the clearance of the cylindrical shaft hole of the passive gear shaft 2; the axial retaining ring 7 is clamped in the retaining ring groove at the end of the passive gear shaft 2 to limit the axial position of the adjacent end cover 5 coaxially sleeved on the middle cylinder of the passive gear shaft 2; it can be a spiral steel wire compression spring or an end cover compression spring 8 of a disc or annular thin leaf spring, which is sleeved on the middle cylinder of the passive gear shaft 2, one end of which is pressed on the end cover compression spring gasket 6 and the other end is pressed on the adjacent end cover 5 so that the two ends of each roller 3 are pressed between the two end covers 5 with an appropriate pre-pressure and the friction force of each roller 3 on the contact surface of the end cover 5 is greater than the maximum thrust of the roller return compression spring 4 on the roller 3.

[0039] The torsion wedging and disengaging process of the utility model during operation is as follows: the two end covers 5 arranged on both sides of the active gear disc 1 are radially fixed in the structure and are never able to rotate radially. When the active toothed disc 1 rotates upward in the positive or negative rotation, there is always one or more rollers 3 clamped at both ends by the two end covers 5 to overcome the thrust of the roller return compression spring 4 installed together with it on the wedge-shaped track groove of the active toothed disc 1 and wedge into the small head space of the wedge-shaped track groove of the active toothed disc 1 to achieve the wedging of the roller 3 under the dead friction angle, thereby driving the passive gear shaft 2 to rotate together and output torque; after the active toothed disc 1 stops rotating, if the passive gear shaft 2 continues to rotate a very small angle along the rotation direction of the active toothed disc 1, the roller 3 can be disengaged from the small head of the wedge-shaped track groove of the active toothed disc 1 and enter the large head space of the wedge-shaped track groove with the assistance of the thrust of the roller return compression spring 4, and the cylindrical working surface of the passive gear shaft 2 is disengaged from the wedge and a gap is maintained, that is, the torque wedging is disengaged, and the passive gear shaft 2 can achieve free idling in the positive and negative rotation directions, thereby realizing that the passive gear shaft 2, i.e., the torque output transmission end mechanism, can be easily and freely rotated manually.

[0040] This manual-automatic roller-type bidirectional gear clutch meets the specific requirements of various practical working conditions of mechanical devices or equipment, including automatic clutch, automatic and manual free switching, etc. When large torque or super-large torque needs to be transmitted, multiple pairs of radially opposite wedge-shaped track grooves can be arranged on the active gear plate 1 to withstand greater wedging pressure and transmit greater torque.

[0041] Obviously, the above embodiments are merely examples for the purpose of clear explanation, and are not intended to limit the implementation methods. For those skilled in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to list all the implementation methods here. The obvious changes or modifications derived therefrom are still within the scope of protection of the invention of the utility model.

Claims

1. A roller type bidirectional gear clutch, characterized in that: It comprises a passive gear shaft (2), an end cover compression spring gasket (6), an end cover compression spring (8), a driving gear disc assembly, two end covers (5) arranged on both sides of the driving gear disc assembly, and an axial retaining ring (7); The end cover compression spring gasket (6), the end cover compression spring (8), the active gear disc assembly, two end covers (5) arranged on both sides of the active gear disc assembly, and the axial retaining ring (7) are sequentially connected with the shaft hole gap and coaxially arranged on the cylinder of the passive gear shaft (2).

2. The roller type bidirectional gear clutch according to claim 1, characterized in that The upper end of the driven gear shaft (2) is a toothed structure, the middle is a cylinder, and the end is provided with an axial retaining ring groove, wherein the axial retaining ring (7) is arranged in the axial retaining ring groove.

3. The roller type bidirectional gear clutch according to claim 1, characterized in that: The active toothed disc assembly is composed of one or more pairs of rollers (3) and roller return compression springs (4) arranged in one or more pairs of wedge-shaped track slots of the active toothed disc (1); The outer ring of the active gear disc (1) is a toothed structure, with a discontinuous cylindrical hole in the center. The cylindrical hole wall is distributed outwardly with at least one or more pairs of semi-open track slots that are arranged oppositely on the circumference and in opposite directions in the radial direction, and form a straight wedge-shaped or arc-shaped wedge-shaped track slot on the outer side with the inner cylindrical surface.

4. The roller type bidirectional gear clutch according to claim 3, characterized in that: The height value H of the two end surfaces of the roller (3) is greater than the thickness value h of the active toothed disc (1). One or more pairs of rollers (3) are arranged together with roller return compression springs (4) in the wedge-shaped track slots formed by the coaxial clearance assembly of the active toothed disc (1) and the passive gear shaft (2), and their axes are parallel to the axes of the latter two.

5. The roller type bidirectional gear clutch according to claim 3 or 4, characterized in that: The two ends of the roller return compression spring (4) are respectively pressed against the side wall of the wedge-shaped track groove end of the active gear plate (1) and the column surface of the roller (3) to apply a radial pre-compression thrust to the roller (3) so that the latter can always maintain a tendency state to disengage from the wedging of the small head of the wedge-shaped track groove.

6. The roller type bidirectional gear clutch according to claim 5, characterized in that: The two end covers (5) are respectively arranged on both sides of the active toothed disc assembly, pressed on the two ends of the roller (3), and assembled together with the clearance fit of the cylindrical shaft hole of the passive gear shaft (2).

7. The roller type bidirectional gear clutch according to claim 6, characterized in that: The end cover compression spring (8) is sleeved on the middle cylinder of the driven gear shaft (2), with one end side pressed on the end cover compression spring gasket (6) and the other end side pressed on the adjacent end cover (5) so that the two ends of each roller (3) are pressed between the two end covers (5) with an appropriate pre-pressure and the friction force of each roller (3) on the contact surface of the end cover (5) is greater than the maximum thrust force of the roller return compression spring (4) on the roller (3).

8. The roller type bidirectional gear clutch according to claim 4, characterized in that: On the cross section of the active gear disc (1), there is at least one point on the continuous track surface projection line of the semi-open wedge-shaped track slot hole, and there is an angle β between the lateral perpendicular line passing through this point on the wedge surface and the line connecting this point and the center of the inner circle, and the value range of the angle β is an angle value within twice the friction dead angle.

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