Classifications

• • 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

Definitions

• the present invention provides a clutch brake, more specifically, a brake assembly that is associated with a rotatable shaft with a driving action, and an outer friction surface. Equipped with a cover assembly pivotally supported relative to the rake assembly, especially for a non-cyclic high-power transmission. About the key.
• connection operation when the number of rotations rises is sudden.
• wear of I-Thing 110 is also large.
• An object of the present invention is to provide a clutch brake capable of increasing a braking torque in accordance with an increase in the U-number of rotations and capable of reducing a wear amount of a friction facing.
• the present invention has a brake-assembly associated with a rotatable shaft with a driving action and an outer friction surface, and is provided so as to be rotatable relative to the brake-assembly.
• the BU recording force system has a pair of substantially disk-shaped force-par elements facing each other.
• An eight plunger connected to the output shaft, which constitutes the brakes assembly, is provided, and a concave part is formed in the outer peripheral part of the eight plunge flange toward the outside in the radial direction of the eight plunge flange.
• a sword that is pushed radially outward of the hug flange with a sword is provided.
• Initial torque that is pressed against one sliding surface That a click latches brake which is characterized that you were interposed a spring member for raw.
• the centrifuge is pressed against the sliding surface of the force assembly by the spring force of the spring part ⁇ , and an initial torque is generated.
• FIG. 1 is a sectional view taken along the line II in FIG. 2 showing an embodiment of the present invention
• FIG. 2 is a partially cutaway front view
• FIG. 3 is a graph showing frictional member wear allowance and torque characteristics.
• FIG. 4 is a graph showing the rotation speed-torque characteristic
• FIG. 5 is a so-called pull type clutch using the clutch brake of the present invention.
• FIG. 6 is a partially cutaway side view showing a conventional example.
• FIG. 1 shows a clutch brake adopting the present invention.
• a substantially annular hub which is engaged with the output shaft 3 (only the center line is shown) and constantly rotates with the output shaft 3. It is.
• An insertion hole # 5 for inserting the output shaft 3 is formed in the inner periphery of the hub 10.
• two opposing projections 11 are formed at predetermined positions of the insertion hole 15, and the projections 11 engage with the output shaft 3 side, and the rotation of the hub ⁇ 0 and the output shaft 3 The direction is unified o
• Hub 10 has eight blang flanges extending radially outward.
• cutouts 14 are formed at six places (only three places are shown) in the circumferential direction on the outer periphery of the haflange 12 as shown in FIG. There.
• a 1-unit 6 centrifugal; F
• F centrifugal
• the side edge 14a of the notch 14 is radially open, a parallel side edge 14'a as shown by a two-dot chain line may be used.
• the outer periphery a 16 a of the gate 6 is formed in an arc shape, and the outer peripheral surface 16 a is pushed in the direction of the arrow P by centrifugal force acting during rotation, and a force pad to be described later. -It comes into sliding contact with the sliding surface S of the assembly -G.
• a compression coil spring 18 (spring member) is interposed between the inner peripheral surface of the gate 16 and the bottom surface 4 b of the notch 14.
• the compression coil spring 18 presses the weight ⁇ 6 against the sliding contact surface S with the spring force in the initial state where the clutch rake is not rotating.
• 3 (Fig. 1) has a function to give an initial torque (array). Note that, instead of the compression coil spring 18, a leaf spring 18a or an opposite leaf spring ⁇ 8b may be used.
• the brake assembly 1B is composed of the above-mentioned solenoid 10, notch 14 and ⁇ : L-it 6 and compression coil spring 18 etc. .
• the retaining cover 19 (canopy element) has an insertion hole 21 for inserting the output shaft 3 on its shaft core side, and an outer peripheral portion thereof. Is formed with a fungus 22 which is a connection portion with the force par 24.
• a through hole 27 for inserting the output shaft 3 is provided on the shaft center side.
• a bent portion 28 which is bent to a substantially L-shaped cross section is formed on the outer peripheral portion.
• the inner peripheral surface of the bent portion 28 is a sliding contact surface S with which the outer peripheral surface 16a (FIG. 2) slides.
• a flange 25 is formed as a connecting portion with the retaining cover-19.
• flanges 25 and 22 are fixed by eight rivets 26 equally spaced in the circumferential direction. It should be noted that, instead of the rivet 26, one of the flanges 22 and 25 may be bent and fixed by "caulking" as is well known. Okay.
• the outer surfaces of the relining cover 19 and the driven cover 24 are respectively provided with annular friction fins 29, 30, which will be described later.
• the above-mentioned clutch rake A slides in the axial direction of the output shaft 3 with the release lever 50, and the pressing of the release bearing 2 is performed. It is located between the surface 56 and the cap 5.
• the clutch 1 performs a release operation, a so-called pull type. It is.
• the cap 5 is fixed to a transmissive circuit; a 4 is a transmis- sion which is not provided with a so-called synchro mechanism in the clutch brake A.
• the output shaft 3 of the section 4 is adapted to activate the inertia brake during shifting. You That is, when the clutch performs a U-raise operation, the output shaft 3 tries to keep rotating with indignation, so that the clutch shaft A applies a brake to the output shaft 3. It is a structure to hang
• the sliding contact surface S acts on the weight 16 side.
• the magnitude of the friction torque is variably controlled by the sum of the spring force of the compression coil spring 18 and the centrifugal force of the weight 16 acting in the direction of arrow P in Fig. 2. Be done. That is, as shown in FIG. 4 showing the change of the torque T with respect to the rotation speed R, even when the rotation speed R is 0, the compression coil spring 18 causes the spring force of the compression coil spring 18.
• the initial torque TO is generated by the frictional force between the outer circumference 3 ⁇ 4 a 6a and the sliding surface S, and the characteristic X that the torque T increases as the rotation speed R increases is exhibited.
• the recess is not limited to the cutout 14, and it is sufficient that the recess slidably accommodates at least the aperture 16 in the radial direction of the hub flange 2.
• the clamp brake of the present invention is composed of two substantially disk-shaped covers which are opposed to each other and constitute a cano-assembly C.
• a hub flange 12 connected to the output shaft that constitutes the brake assembly B is provided between 19, 24 and the cover (element), and the hub flange 12 is connected to the hub flange 12.
• a notch 14 (recess) is formed, and this notch 14 is provided with an centrifugal force radially outward of the hub flange ⁇ 2.
• a weight 16 is pressed between the hap flange 12 and the sliding surface S of the force power assembly C facing the outer peripheral surface of the weight 16 for initial torque generation.
• the compression coil spring 18 (spring member) is interposed, the magnitude of the friction torque acting from the sliding surface S side to the weight 16 side is reduced by the spring force of the compression coil spring 18. In addition, it can be variably controlled by the centrifugal force of weight 16 acting in the direction of arrow P in Fig. 2.
• the initial force is generated by the frictional force between the outer peripheral surface 16a and the sliding contact surface S due to the spring force of the compression coil spring 18.
• the torque TO can be generated, and the torque T increases quadratically with an increase in the rotation speed R, in response to the indignation of the output shaft 3 that increases with the increase in the rotation speed R. Can generate large brake torque.
• the output shaft 3 can be stopped quickly to reduce the amount of wear of the friction facings 29, 30 and to perform the shifting operation even with the transmission 4 without the synchro mechanism. It can be easier.
• the clutch brake according to the present invention is useful as various automotive clutch brakes.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Braking Arrangements (AREA)
• Mechanical Operated Clutches (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=16392420

Family Applications (1)

Country Status (2)

Families Citing this family (2)

Citations (2)

• 1986
  • 1986-08-25 JP JP19851586A patent/JPS6357929A/ja active Granted
• 1987
  • 1987-08-05 WO PCT/JP1987/000588 patent/WO1990008269A1/ja unknown

Patent Citations (2)

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