KR820002385Y1 - Slipping clutch mechanism - Google Patents

Abstract

No content.

Description

Slipping clutch mechanism

1 is a vertical cross-sectional view of a blower having a clutch mechanism according to the present invention.

2 is a partial exploded view of a part of the first degree blower showing the clutch mechanism in detail,

3 is a vertical sectional view of a portion of the first FIG. Blower showing the clutch in a rotationally engaged position,

4 is a vertical sectional view of a portion of the first FIG. Blower showing the clutch in a rotationally disengaged position.

The present invention relates to a sleeping clutch mechanism suitable for use in a head-mounted blower that provides airflow in a gyratory distribution mode.

In Australian Patent No. 459,701, a blower is described and claimed which allows a blower head to be fixed but permits air discharge in a swirl distribution mode. The term “swirl distribution modality” refers to an air flow distribution modality such as that generated by a blower that uses a mechanism to mechanically drive the blower-motor assembly in a traditional or pivotal manner, except that the flow is thinner and hardly spirals. Means. The blower described in the Australian patent has a blower vane assembly, an electric motor for driving the blower vane assembly, means for axially providing airflow from the wing assembly, from the wing assembly and axial airflow means to the flow path of air. Consisting of an air guide grate mounted and driven by a motor to rotate at a slower speed than the wing assembly speed, the grate being arranged in parallel with the air stream and arranged in other arts such that the air flow is guided by the grate in a swing distribution mode. Has a louver of.

The blower described in the Australian patent has a clutch mechanism that operates to interrupt drive to the grate when rotation of the grate is interrupted. The mechanism has three spring steel leaf springs extending rearward from the same angled positions of the rear end of the central hub installed in the grate. Further, the grate and the hub are mounted to move coaxially to the drive shaft of the electric motor for the blower. The drive shaft has a coaxial clutch ring and the grate is mounted so that it can be moved from the front non-driven position to the rear position that connects the rotational drive action to the grate, in which the free trailing ends of the spring are clutched. It is arranged in front of the ring away from the clutch ring. In such rearward movement, the free end of the spring engages the inclined circumferential cam surface of the inclined front end of the front end of the clutch ring so that the free ends are far away in the radial direction. As it moves further rearward, its free ends rest on the cam surface to engage the circumferential annular groove of the clutch ring. The bottom of the groove is meandered so as to form a plurality of radially extending notches, which are separated by radially outwardly extending projections of the groove bottom and at equal intervals around the axis of the drive shaft. Away. The trailing free ends of the spring enter into appropriately arranged notches of these notches, thereby locking the hub and clutch ring with each other to rotate the grate with the drive shaft. If the rotation of the grate is hindered when the clutch mechanism is engaged, the drive shaft can continue to rotate without transmitting excessive driving force to the grate, and the free ends of the springs engage the successive protrusions of the groove bottom. The cam actuation is repeatedly pressed outward against the spring bias.

This clutch mechanism is satisfactory in use, but has a disadvantage in that the structure is relatively complicated, mass production is difficult, and the price of the blower is increased by the assembling work of the complicated clutch. In particular, the assembly of the clutch mechanism

(1) leaf springs each attached to a hub,

(2) clutch ring assembled on motor drive shaft,

(3) a hub disposed in place such that the free ends of the spring extend coaxially with the drive shaft while being disposed in the notch of the groove of the clutch ring;

(4) a screw inserted through the opening of the transverse wall of the hub into the screw hole of the shaft to prevent the grate from escaping from the drive shaft under the forward pressure of the air provided by the blower,

Etc. These assembly operations are difficult to automate.

Moreover, the apparatus of the Australian patent can sometimes fail due to the loosening of the screw holding the hub on the rotating shaft, and this disadvantage can be eliminated by process inspection, but such a structure is not completely satisfactory.

Accordingly, it is desirable to provide a clutch mechanism for use in a blower of the type described in Australian Patent No. 459,701, which is relatively simple in structure and can be mass produced.

It has been proposed to provide the clutch with a spiral spring-type drive transmission member mounted coaxially over the drive shaft for the grate to frictionally engage the outer surface of the drive shaft for transmitting the rotational movement of the drive shaft to the spring. This spiral spring has an end extending radially outward of the drive shaft. In addition, the hub of the grate has a protrusion that is engaged at the end of the spring upon rotation of the drive shaft and is arranged to cause or allow rotation of the hub and the grate. The frictional engagement between the spring and the drive shaft causes the drive shaft to rotate in the normal rotational direction of the grate without imparting a rotational motion to the spring when a certain restraint on the rotation of the grate is applied to the grate.

This normal direction of rotation is the direction of unwinding the spiral spring when the grate is prevented from rotating. When the drive shaft rotates in such a preferred direction and the grate is held incapable of rotation, the pressure at the spring end against the protrusion due to the rotation of the drive shaft relaxes the engagement between the spring and the drive shaft and partially frees the spring. Thus, the drive shaft keeps rotating without rotating the spring. In addition, the extension arm of the spring is resilient so that when the grate is fixed and the drive shaft is rotated in a second direction which winds up the spring and increases the frictional engagement between the spring and the drive shaft, the end of the spring permits continued rotation of the drive shaft. It is elastically deformed to pass through the projection on the hub of the grate. This action also occurs, for example, when the grate is caused to rotate faster than the drive shaft.

The drive shaft also preferably has a groove that engages at least partially so that at least one of the windings of the spiral spring limits the axial movement of the spring relative to the drive shaft. In this proposal, the grate is movable in the axial direction of the drive shaft, and the blower is provided with an annular casing portion engageable with the outer axial annular portion of the grate when the hub is moved axially in a direction that frees the clutch mechanism to disconnect the drive of the grate. Have A releasable fixing member is provided to operate to retain the annular portion of the casing while engaged to give a certain restraint to the grate, so that the drive shaft enables the grate to be fixed without disconnection of the motor and decoils the windings of the spring. .

Although many types of such mechanisms have been developed or proposed, the present invention is particularly useful for blowers, is economical to manufacture, easy to install at the manufacturing stage of the article in which the clutch mechanism is to be used, and improves the overall operation of the article. It is an object to provide an improved slipping clutch mechanism.

Other objects of the present invention are apparent from the following description taken in conjunction with the accompanying drawings. The blower shown in the drawing has a plastic casing 1 formed of two parts formed by an inner wall 9 whose passages communicate with the air inlet opening 2 at the rear of the casing and the air outlet opening 3 at the front of the casing. Have. The casing has an annular recess 4 surrounding the introduction opening 2, which recess receives the base of the plastic cage 5 held in the casing by screws 6, and the cage Has a plurality of air intake openings 7 through it. The blower motor M is disposed in the passage inner wall 9 and is supported by the plastic enclosure 12 supported by the radial vanes 11 extending between the plastic enclosure 12 and the passage inner wall 9. Attached. The motor has an output shaft 13 and one end of the shaft facing the introduction opening 2 supports the blower vane assembly F.

The other end of the output shaft is connected to the reduction gear box G, which is embedded in the motor body and has a coaxial output shaft 0. The output shaft supports a circular air guide grate 17, which is slidable in the longitudinal direction to the output shaft 9 and is independent of the rotation of the axis 0. The grate 17 is rotatably supported by a central hub 18 mounted on a shaft 0, has a concentric rim 19, and a number of parallel louvers between the rims. 20 is connected. The louvers are arranged in groups arranged at different acute angles with respect to the airflow direction from the vanes 11. The grate 17, including the hub, is formed from an integral plastic molding. The flushing mechanism 21 is provided to connect the output drive shaft 0 with the grate 17 and the hub 18.

It was found that the grate of the following structure was satisfactory. That is, the central hub is about 5cm in diameter and the rim is about 33cm in diameter. The louvers are three groups: the first group of six louvers positioned near a part of the rim and arranged at 0 ° to the airflow direction, the second group of seven louvers arranged at 15 ° to the airflow direction, and the airflow direction Is arranged in a third group of six louvers arranged at 30 [deg.], And the spacing between the groups is slightly larger than the spacing between adjacent louvers in the groups. The hub 18 has an annular skirt 23 which is spaced about the axis 0 at a predetermined interval and protrudes concentrically (away from the drive mechanism).

The clutch mechanism 21 is shown well in FIGS. 2-4. On the inner surface of the skirt 23, pads 24 spaced apart by a pair of gaps that partially form the grooves 25 are arranged. The pad is formed in a skirt body that extends slightly behind its ends. The skirt 23 projects forward from the wall 26 which centers the opposing protruding ring 27 used for mounting the hub and grate. The mounting ring 27 incorporates a porous sleeve bearing 28 that supports a rotating grate assembly on an axis 0 extending from the output shaft of the gearbox G (FIG. 1). The pad 24 and the groove 25 are located on the inner surface of the skirt 23 adjacent the wall 26. As will be described in detail later, in the illustrated embodiment, pads 24 and grooves 25 are provided spaced apart from each other in pairs.

An annular molding 30 having the form shown in FIGS. 2-4 is provided. This molding includes a set screw 32 having a head 24 having teeth formed thereon. This head 34 provides firm fixation of the set screw when the head is molded with the molding 30 and the screw is integral with the molding.

A hole 36 is provided at the end of the drive shaft 0, and the hole is adapted to accommodate the body portion in which the screw shaft groove of the screw 32 is formed. When the molding 30 in which the screw 32 is integrated is screwed into the hole 36, the molding 30 becomes a driving member that rotates together with the driving shaft 0. The molding 30 is fitted in the skirt 23 of the hub 18 and is adapted to rotate.

The hub 18 of the grate 17 is rotatably mounted to the end of the drive shaft 0 by the sleeve bearing 28. Such mounting allows the grate 17 to rotate independently of the drive shaft 0 and to slide longitudinally on the drive shaft. The grate 17 can be removed for cleaning by loosening the molding 30 and the screw 32 and removing the grate from the drive shaft 0.

A disc spring 38 is provided to be mounted to the screw 32 at the end of the drive shaft, the disc spring having a radius interconnecting the drive member, i.e. the molding 30, with the driven member, i.e. the hub 18 and the grate 17. To form a directional means. The disk spring 38 is preferably of the over-the-center snap-achon type as shown in FIG. Three radially inwardly extending fingers 40 project inwardly toward the center. The inner ends of these three fingers form the hub of the disk. The body of the disc spring has an annular portion 42 having a structure similar to a Belleville Washer. Three protrusions 44 protrude radially outward from the annular portion 42 in the direction opposite the finger 40. The protrusions 44 each have a notched tip 46.

Lugs 48 are provided in a raised manner so as to project at right angles from one side of a portion of the disc spring 38. The upright disc 48 is provided along each of the three projections 44 and is connected to the side edges of each projection. The disc spring 38 is an elastic member having the shape shown, made of tempered steel and three upright lugs 48 (120 °) apart. The grate 17 is movable axially on the drive shaft 0 from the position shown in FIG. 3 to the position in FIG. 4, and the drive of the grate in the position in FIG. 3 is achieved as described later, In position, driving is prevented. Movement between the driven and non-driven positions may cause the rim of the grate to disengage, or to remove the rim 19 from engagement with the annular portion 50 with the grate drive engaged. 19 is achieved by pushing inward or pulling outward at hub 18 to engage the annular portion 50 of casing 1 (FIGS. 1 and 2).

The hub of the disk spring 38 mounted at the end of the drive shaft 0 to the screw 32 is fixed in this position in the axial direction of the drive shaft 0. The hub is thus a pivot point or center point and the disk spring 38 stores oil on either side of the seam point by the axial movement of the hub 18. The protrusion 44 extends radially to engage the groove 25 and the tip 46 in a mutually coupled manner. This mutual coupling is achieved by the engagement of the wide protrusions 44 to the ends of the pads 24, the tips 46 being formed on the inner wall surface of the skirt 23 as shown in FIGS. 3 and 4. Extend into the groove 25. Thus, when the hub 18 is pressed towards the drive shaft 0, engagement with the tip 46 moves the spring past the center to the position shown in FIG. 4 and when the hub is pulled outward (third Fig. 2) is reversed by the action of the pads 24 on the protrusions 44.

The inner surface of the molding 30 has one or more stops 52 which receive the lugs 48 when the hub 18 is pulled outward, ie when placed in the drive position. In the embodiment shown, the stop 52 is provided in the form of a radially extending slot on the inner surface of the molding 30. Six stops are provided at 60 ° intervals. Of course, other forms of stops may be provided. Thus, when the hub 18 is pulled outward to engage the grate with the drive so that the grate rotates, the lugs are held against its stop by spring forces, so that the mutually coupled tips as shown in FIG. The hub 18 and the driving member 30 are connected to each other via 46. This connection is broken when the hub 18 is pressed in as shown in FIG.

The surface of each lug 48 is angled to impart a cam action between the lug and the stop. Thus, when the grate 17 is restrained from turning by interference with the grate, slippage occurs at the engagement of the stop and lug by the elasticity of the disc spring 38 and the angular-surface of the lug 48, The rotary drive member 30 is rotated without and irrespective of the driven member (the hub 18. The drive lug 48 only slips out of the stop 52, The rigidity of the disc spring 38 hanging around the stops until the stopping force is removed and the normal drive is restored should be such that the user's finger is inserted into the grate 17 to stop the movement of the grate. The relationship between the structures and their stops is such that even when applied to the cam action force in the rotational direction, the lugs are cam-moved out of engagement with the stops, thus allowing the user to push the grate by hand in either direction. When a force, such as rotating, is applied to the grate and the hub, the lug only acts as a cam to get out of engagement with the stop and the drive shaft (0) continues its drive without overloading the motor or damaging the person or device. do.

In this structure, the passage of air through the grate 17 imparts rotational energy to the grate, which tends to rotate faster than the drive shaft 0, even at low blower speeds. Thus, during operation of the device, the engagement of the stop 52 and the lug 48 restrains the grate and rotates only in one piece with the drive member 30 and the drive shaft 0. On the other hand, the drive shaft 0 is the output shaft of the reduction gear device G, and thus rotates at the motor speed and at a slower speed than that of the shaft 13. The satisfactory speed of the output shaft 0 and the rotational speed of the grate 17 are 6 rpm.

When continuous airflow is required in an area, the grate 17 is pressed in to disengage the clutch mechanism to the position shown in FIG. The grate 17 is pressed by the rigidity of the spring 38 and is supported by the annular portion 50 of the casing. In this position the lug 48 is completely disengaged from the stop 52, allowing the drive member 30 to rotate freely without causing the rotation of the grate 17. However, by the pressure from the spring 38, the contact of the grate 17 with the blower casing is suitable to prevent free rotation of the grate, which may be caused by the airflow through the louver. It can also be passively placed at any desired angular position so that the airflow direction is constant because it is free from the driving force on the grate.

This clutch should be allowed to slip when a wing force that reacts to or accelerates the drive shaft 0 is applied to the grate 17. Although this is primarily for human safety, this is desirable because the gear deceleration of the drive motor gearbox G causes a large torque that can damage the plastic grate 17 when the clutch is not allowed to slip when needed. will be.

In use, the helical air flow from the blower vane F passes through the vane F and is straightened axially.

It is then redirected by the air as it passes through the grate louver 11. When the grate 20 is pulled into the drive position, the grate directs the air in a nearly identical distribution to that of the swing head blower. The only real difference in the generated airflow is that it is axial rather than spiral as in a conventional swing head blower. This is believed to be an advantage rather than a disadvantage.

Using the particular louver structure as described above, the generated airflow pattern is represented by a chart of standard tests and the area of that airflow type has a diameter slightly larger than that of an equivalent slewing head blower. In that form of air, air always travels in the central part of the whole area.

According to the present invention, a blower wing assembly, an electric motor for driving the blower wing assembly, a means for providing air flow in the axial direction from the blower wing assembly, an air guide grate mounted in a passage of air flow from the blower wing assembly, a motor A blower is provided that includes a clutch mechanism operable to connect a drive output from the coaxially mounted driven member to support the grate for rotating the grate at a speed lower than the blower vane assembly speed. The grate has a plurality of louvers installed to direct the airflow in a swing distribution manner, and the clutch mechanism has a drive member mounted to the drive output unit in addition to the driven member. The driven member is independent of the driving member. The clutch also has a single elastic member which extends radially in the middle of the driven member and the drive member to transmit the driving force therebetween and engage them with a force suitable for rotating them together. The elastic member has a facility to slip the engagement and cause the rotary drive member to rotate independently of the driven member when a predetermined rotational suppression is applied to the driven member or an external driving force is applied to the driven member.

Claims (1)

A rotary drive member 30 connected to the drive shaft 0, a driven member 18 coaxially mounted to the drive shaft and independent of the drive shaft, extending radially between the drive member and the driven member and between them; It consists of a single elastic member 38 which engages both to transmit the driving force and to rotate the members together with each other, the elastic member 38 slips the engagement of the driving member and the driven member and the predetermined rotational suppression And a facility (48) which, when applied to a driven member (18), causes the rotary drive member (30) to rotate without imparting a rotary motion to the driven member.