WO1996001380A1 - Frein normalement serre - Google Patents

Frein normalement serre Download PDF

Info

Publication number
WO1996001380A1
WO1996001380A1 PCT/CN1995/000055 CN9500055W WO9601380A1 WO 1996001380 A1 WO1996001380 A1 WO 1996001380A1 CN 9500055 W CN9500055 W CN 9500055W WO 9601380 A1 WO9601380 A1 WO 9601380A1
Authority
WO
WIPO (PCT)
Prior art keywords
block
brake
driving
braking
disc
Prior art date
Application number
PCT/CN1995/000055
Other languages
English (en)
French (fr)
Inventor
Xingyun Xie
Original Assignee
Xingyun Xie
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN95106603A external-priority patent/CN1067467C/zh
Priority to JP50359996A priority Critical patent/JP3959109B2/ja
Priority to HU9700002A priority patent/HU220502B1/hu
Priority to CA002194285A priority patent/CA2194285C/en
Priority to DE69531687T priority patent/DE69531687T2/de
Priority to AU27844/95A priority patent/AU697266B2/en
Priority to EP95923172A priority patent/EP0769634B1/en
Priority to AT95923172T priority patent/ATE248996T1/de
Application filed by Xingyun Xie filed Critical Xingyun Xie
Priority to KR1019960707591A priority patent/KR100297569B1/ko
Priority to PL95318103A priority patent/PL176385B1/pl
Priority to BR9508214A priority patent/BR9508214A/pt
Priority to UA97010044A priority patent/UA44895C2/uk
Priority to MX9700115A priority patent/MX9700115A/es
Priority to US08/765,994 priority patent/US6374963B1/en
Publication of WO1996001380A1 publication Critical patent/WO1996001380A1/zh
Priority to NO19965600A priority patent/NO327166B1/no
Priority to FI965288A priority patent/FI115792B/fi
Priority to BG101179A priority patent/BG62372B1/bg

Links

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
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
    • F16D63/008—Brakes acting on a linearly moving member
    • 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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • 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
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/186—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with full-face force-applying member, e.g. annular
    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
    • 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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/024—Braking members; Mounting thereof the braking surface being inclined with respect to the rotor's axis of rotation at an angle other than 90 degrees, e.g. comprising a conical rotor
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • F16D2121/16—Mechanical for releasing a normally applied brake
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/32—Cams; Levers with cams acting on one cam follower
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/64—Levers
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/66—Wedges
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/001—Auxiliary mechanisms for automatic or self-acting brake operation
    • F16D2127/005—Auxiliary mechanisms for automatic or self-acting brake operation force- or torque-responsive

Definitions

  • the invention relates to a mechanical normally closed braking device for braking a moving object.
  • the so-called normally closed braking device here means that when the driving member and the driven member are in a stationary state, the braking device is always in a braking state.
  • Existing brakes whether they are mechanically powered or electromagnetic, or electromagnetic hydraulic, require a power source device with a complex structure and a considerable energy consumption. Like the existing normally closed brake, it requires an additional force source device to provide external force to release the normally closed brake.
  • Another example is the electromagnetic brake brake.
  • the normally closed state uses spring force as the braking force to brake the object. When the object needs to run or rotate, it needs to energize the electromagnet to generate electromagnetic force to overcome the spring. Force to release the normally closed braking state.
  • the braking device is composed of an additional force source device, a follow-up mechanism, a braking mechanism, and a booster mechanism.
  • the main braking external force during braking is converted from the inertial force of the braked object when it is in motion. .
  • This device has the characteristics of short braking time, fast mitigation speed, and reliable work.
  • an additional power source device is still required to provide braking operating force in normal motion. When the additional power source device is working, it still needs to consume a certain amount of energy.
  • the present invention proposes a further development and significant improvement of the prior art including the above-mentioned patents, and proposes a compact structure, which can realize braking or releasing control in the normal running state or stationary state without requiring an additional force source. Moving device.
  • Yet another object of the present invention is to provide a device for realizing braking or alleviating braking by using relative motion occurring between a driving member and a driven member within a period of time after starting transmission and stopping transmission.
  • a further object of the present invention is to provide a device for realizing braking or alleviating braking by using the concave-convex mating surface of a connection mechanism between a driving member and a driven member.
  • the present invention provides such a normally-closed brake, which includes a driving member, a driven member, a connection mechanism capable of driving the driven member to move the driven member in a first direction, a fixed seat with a friction surface, and a connection to the driven member.
  • a braking member that can be fitted or disengaged with the friction surface on the fixed seat to realize braking or easing of the driven member moving in the first direction;
  • the invention is that the connecting mechanism is disposed between the driving member and the driven member, and includes an action block that can move with the driving member in the first direction, and a first block that can perform the first movement with the driven member.
  • a driving block capable of generating a relative displacement in a second direction with respect to the driven member in the directional movement;
  • the action block and the driving block have a relatively movable matching structure.
  • the driving member obtains the main power or loses the main power, they can generate such relative motion, which causes the driving block to be displaced in a second direction relative to the driven member. , So as to achieve the relief of the braking of the follower or the braking of the follower;
  • the connecting mechanism further includes a limiting mechanism for limiting the relative moving distance of the acting block and the driving block, and bringing them into a common motion state after braking or easing is completed.
  • the movement in the first direction may be a rotational movement.
  • the limiting mechanism may include a spring that presses the driving block against the acting block to ensure that after the relative movement of the acting block and the driving block, a sufficient force capable of common movement is generated between each other.
  • the limiting mechanism may further include: a disc-shaped member is connected to the driving member, and a plurality of pins are provided outside the center of the disc-shaped member; and the driven member is further included.
  • a disc-shaped member on the upper portion corresponds to the position of the pin shaft.
  • the disc-shaped member of the follower is provided with a plurality of long holes in the arc direction, and the pin shafts can move relative to each other in the long holes. And abut one end of the slot.
  • the driving member and the driven member may be arranged up and down, and the limiting mechanism includes a disc-shaped member connected to the driving member, and the disc-shaped member is provided outside the center of the disc-shaped member.
  • a plurality of pins; further comprising a disc-shaped member on the driven member, a plurality of long holes in the direction of the arc are provided on the disc-shaped member of the driven member corresponding to the position of the pin, The pin shaft can move in the long hole and finally abut against one end of the long hole.
  • the cooperation structure that generates relative movement between the action block and the action surface of the drive block is a cam engagement structure, and any one of the action surface of the action block and the action surface of the drive block For the cam surface.
  • the driving block can be displaced in a second direction relative to the acting block, thereby achieving braking or easing the braking.
  • the action surfaces of the action block and the drive block may both be cam surfaces.
  • the displacement in the second direction by the driving block may be in the axial direction of the rotary follower, that is, the brake has a displacement generated in the axial direction of the rotary follower.
  • Drive block displaced in the second direction.
  • the displacement in the second direction by the driving block may be driven along the rotation
  • the radial direction of the member, that is, the brake has a driving block that is displaced in the second direction in the radial direction of the rotary follower.
  • the disc member of the braking member and the follower member may be an integrated structure, and the integral structure of the disc member and the disc member includes a disc having an internal ring gear.
  • Body and core, between the disc body and the core body, a compensation mechanism and a sliding key that can move the disc body and the core body in a first direction may be provided, and the compensation mechanism includes a A groove, a tooth block located in the groove and capable of cooperating with the disc body, and a spring located between the tooth block and the bottom of the groove.
  • both end faces of the action block along the axis of the rotation follower may have a concave-convex action surface, and simultaneously use the two end faces to cooperate with two drive blocks at the same time; that is, That is to say, the two end faces in the brake which have the axial direction of the rotation follower are the action blocks of the mating structure which respectively cooperate with the two driving blocks.
  • the friction surface on the fixed seat may be a tapered surface, a flat surface, or a cylindrical surface
  • the braking surface on the brake member may also be a tapered surface, a flat surface, or a cylindrical surface.
  • the movement in the first direction may also be a linear movement; and in the brake, the displacement in the second direction by the driving block may be along the vertical of the linear movement follower Direction; that is, the brake has a vertical movement of the follower in a linear motion; the i-direction produces a second-direction displacement of the driving block.
  • FIG. 1 is a cross-sectional view of the first embodiment of the present invention along the line A-A in FIG. 2, showing the structure of a sliding pin, a sliding hole, and a connecting rod;
  • Fig. 2 is a sectional view taken along line B-B in Fig. 1;
  • FIG. 3 is an axial view of a force conversion mechanism
  • FIG. 4 is a sectional view taken along the line G-G in FIG. 3;
  • FIG. 5 is a developed view of a concave-convex mating surface of an action block and a drive block;
  • FIG. 6 is a cross-sectional view of a second embodiment of the present invention along the line C-C in FIG. 7;
  • FIG. 7 is a cross-sectional view taken along line D-D in FIG. 6;
  • FIG. 10 is an axial sectional view of a third embodiment of the present invention.
  • FIG. 11 is a top view of the present invention applied to a speed reducer
  • FIG. 12 is a sectional view taken along line M-M in FIG. 11;
  • FIG. 13 is a sectional view taken along the line N-N in FIG. 11;
  • FIG. 16 is a sectional view of a seventh embodiment of the present invention.
  • 17 is a cross-sectional view taken along the line K-K in FIG. 16;
  • FIG. 18 is a sectional view taken along line 6H-H in FIG. 16;
  • Fig. 19 shows an eighth embodiment of the present invention.
  • Figures 1 to 5 show a first embodiment of the present invention.
  • the normally-closed brake according to Embodiment 1 of the present invention includes a fixed seat 1, a braking member 2, a braking spring 3, a force conversion mechanism 4, a driven member 9, and a driving member 11.
  • the structure and interconnection relationship are as follows:
  • the fixing base 1 is provided with a brake pad 6 (the two are integrated), and the braking friction surface 8 of the braking member 2 may be a flat surface or a tapered surface, which is disengaged from the friction surface on the brake pad 6 to realize braking or mitigation.
  • Fig. 2 shows a state where the friction surface of the brake member and the friction surface of the brake pad 6 are in close contact, that is, in a braking state.
  • the braking member 2 has a sliding hole 7 in the arc direction and a shaft sleeve 10 for connecting the passive follower 9.
  • the sliding hole 7 has a certain length in the arc direction. Since the brake member 2 is integrated with the shaft sleeve 10, when the brake member 2 is in close contact with the brake pad 6 and is in a braking state, the shaft sleeve 10 is used to brake the passive follower 9 Moreover, through the cooperation between the sleeve 10 and the driven member 9, the braking member 2 can slide relative to the driven member 9 in the axial direction.
  • the connecting rod 12 is mounted on the braking member 2 at the end, and the spring 3 is mounted on the end of the connecting rod.
  • the spring force acts on the braking member 2.
  • the brake member 2 comes into close contact with the brake pad 6 due to the action of the spring 3. (The role of the brake pad 16 and the spring 20 in Fig. 1 will be described later).
  • the force conversion mechanism 4 is composed of an action block 13 connected to the driving member 11 and a driving block 14 fixedly connected to the braking member 2 (see FIGS. 3 to 5).
  • the contact surface between the action block 13 and the driving block 14 is a convex and concave contact surface 15 (equivalent to convex
  • the follower in the wheel mechanism also has a cam surface).
  • the sliding pin 5 is located in the sliding hole 7 of the braking member 2. One end is connected to the driving member 11 and the other end is matched with the action block 13 in the force conversion mechanism 4 (see FIG. 1).
  • the slide pin 5 is relatively movable within the slide hole 7. By using the displacement generated by the sliding pin 5 in the sliding hole 7, the operation block 13 is rotated, and the braking member 2 can be driven to move by the driving block 14.
  • the active member 11 When an active element such as a motor is started to start operation, the active member 11 starts to rotate with the main power and drives the sliding pin 5 to move within the sliding hole 7.
  • the other end of the sliding pin 5 is provided with an action block 13 in the power conversion mechanism. Rotating, the action block 13 generates thrust to the driving block 14, and the driving member 14 is used to move the braking member 2 outward to gradually release the brake.
  • the passive follower 9 When the braking state is not completely released, the passive follower 9 is still at a standstill. .
  • the sliding pin 5 When the sliding pin 5 is moved to one end of the sliding hole 7, the braking state is completely released. At this time, the sliding pin 5 acts as a torque transmitting shaft to drive the brake member 2 to rotate, and the passive follower 9 connected to the brake member sleeve 10 then moves normally.
  • the displacement of the sliding pin 5 in the sliding hole 7 causes the driving block 14 to rotate, so that the driving block 14 drives the braking member 2 Move out to release the brake.
  • the action block 13 in the force conversion mechanism rotates due to the action of the sliding pin 5 and the limit effect of the slide hole 7 ensures that the action on the action block 13
  • the convex section of the contact with the convex section of the driving block 14 reliably, so that the brake is maintained in a released state.
  • the process of restoring the normally closed braking state is to cut off the power of the active component (such as a motor) when braking is needed.
  • the active component 11 is decelerated due to the loss of main power due to the counter torque during operation.
  • a displacement in the slide hole 7 is generated in the opposite direction to the starting position, so that the driving block 13 is reversed accordingly, so that the convex section on the action block 13 moves toward the concave section on the drive block 14 until the action block 13 is moved relative to the drive block 14.
  • Thrust elimination Since the brake spring 3 acts on the brake member 2, the brake member 2 contacts the brake pad 6 due to the pressure of the spring 3, and generates frictional resistance to stop the brake member 2 from being connected to the brake member 2 and the shaft sleeve 10.
  • the passive follower 9 is then braked, that is, the braking state is achieved.
  • Figs. 6 to 9 show a second embodiment of the present invention, in which the same or similar parts as those in the above embodiment are designated by the same reference numerals.
  • a brake member 16 corresponding to the brake member 2 is provided on the other side of the brake pad 6, and the braking friction surface of the brake member 16 corresponds to the friction surface of the other side of the brake pad 6 and is disengaged.
  • the other end of the action block 13 is provided with a drive block 18 (see FIGS. 4 and 5) corresponding to the drive block 14.
  • the convex and concave contact surfaces 19 of the action block 13 and the drive block 18 are symmetrical with the contact surface 15.
  • a sliding key 17 is provided which can move and stop the two members simultaneously, and the two braking members can move relative to each other in the axial direction along the sliding key 17. .
  • Both ends of the connecting rod 12 are connected to the braking member 2 and the braking member 16, respectively.
  • the ends of the connecting rod 12 connected to the braking member 2 are provided with a spring 3, and the elastic force of the spring acts on the braking member 2.
  • the other end of the connecting rod 12 may be provided with a spring 20 (see FIG. 2) commensurate with the spring 3, and the spring force of the spring acts on the braking member 16.
  • the other end of the connecting rod 12 can also be fixed on the braking member 16, and the spring 3 acts on the braking member 16 through the connecting rod 12 (see FIG. 7). Friction plates are provided on the braking friction surfaces of the braking member 2 and the braking member 16.
  • At least two sliding pins 5 and corresponding sliding holes 7 are provided, and are symmetrically and uniformly distributed.
  • At least two connecting rods 12 for connecting the braking member are provided. It is arranged symmetrically and evenly; there are two brake springs 3 in this embodiment, and two or more brake springs 20 may or may not be provided.
  • the working process of the second embodiment of the present invention for releasing the braking state is that the action block 13 rotates with the rotation of the sliding pin 5 when the driving member is activated by the main force, and generates outward outwards to the driving blocks 14 and 18 at both ends.
  • the thrust force moves the brake member 2 and the brake member 16 outward at the same time and leaves the brake pad 6 to realize the release of the normally closed brake and the normal operation of the passive follower.
  • the action block 13 rotates in the opposite direction with the sliding pin 5 to move the convex section on the action block toward the concave section of the driving block, the thrust is eliminated, and the brake spring 3 and the brake spring 20 act on The braking member 2 and the braking member 16 or the braking spring 3 acts on the braking member 2 and the braking member 16 through the connecting rod 12 at the same time, so that the two braking members move inward at the same time and tightly contact the brake pads. 6. Restore the normally closed braking state.
  • both the braking member 2 and the braking member 16 can also be composed of a disc body 21 and a core body 22 with internal teeth.
  • a brake compensation mechanism 23 and a A feather key 24 that enables the disc body to run or stop at the same time as the core body.
  • the feather key 24 is also used to ensure the balance of the disc body along the core mounting structure.
  • the braking compensation mechanism on the braking member 2 and the braking member 16 are symmetrically disposed.
  • the brake pad 6 has a double-plate structure and is slidably coupled by the support shaft 30.
  • a connecting inner plate body 29 is also provided on the connecting rod 12 for increasing braking Friction.
  • the brake compensation mechanism has an improved ring gear structure, that is, a ring gear 26 is provided on the inner ring of the disc body 21, and a tooth block 25 is provided on the circumference of the core body 22 (see FIGS. 8 and 9). 25 has external teeth matched with the ring gear 26, and the outer side of each tooth is an inclined plane, and the inner side is a vertical plane perpendicular to the transmission axis.
  • the ring gear 26 and the tooth block 25 can be matched with a thread surface.
  • a spring 28 is provided at the bottom of the sliding key 24. The sliding key 24 can be adjusted by screws, so that the disk body 21 and the core body 22 can rotate along the thread as a manual adjustment of the friction clearance.
  • the tooth block 25 is installed in a groove 27 formed in the circumferential direction of the core body 22, and a spring 27a (see FIG. 8) acting on the tooth block 25 is provided at the bottom of the groove 27.
  • the tooth blocks 25 are arranged in pairs. In this example, there are four pairs and a total of eight pieces, of which some are evenly arranged in pairs (four pieces in this example, not blackened in Figure 6) are in full contact (see Figure 8). In addition, the evenly arranged pairs (the four blackened blocks in Fig. 6) are partially contacted (see Fig. 9). The full contact is in the working state. That is, when the core of the brake member is driven by the force conversion mechanism and moved outward, the disc is driven to move outside to release the brake.
  • the brake spring acts on the core body, bringing the disc body into tight contact with the brake pad 6 to achieve braking.
  • the tooth block 25 whose teeth are partly in contact is in a compensation state. After the friction plate on the disc body is worn to a certain extent, the core 22 moves relative to the disc body 21 when it moves outward under the action of the driving block.
  • the tooth block 25 overcomes the force of the spring 27a and moves down inside the recess, and the teeth on it slide into the next ring gear of the disc body, that is, in full contact, and becomes the working state, and the original full contact tooth block becomes Compensation status for partial contact.
  • the compensation mechanism 23 described in this embodiment 2 can be used in other brakes of the present invention in which the brake member is a disc type, as described in Embodiments 3, 4, 5, 6, etc. .
  • Fig. 10 shows a third embodiment of the present invention. Also, the parts which are the same as or similar to those in the above embodiment are designated by the same reference numerals.
  • FIG. 10 is a sectional structural view of the embodiment along the axial direction.
  • the fixed seat is composed of three connecting shafts 31 and two side plates 32 connected to both ends of the three shafts.
  • the brake pad 6 is composed of two split discs 33, both of which are fixed on the connecting shaft 31, and the brake member 2 and the brake member 16 are respectively connected with The two-piece disc 33 of the brake pad 6 corresponds.
  • the brake piece 2 and the brake piece 16 and the two separated discs 33 may be provided with a brake pad 34 and a follower inner disc brake piece 35.
  • the brake pad 34 is connected to the connecting shaft 31 and can move along the shaft.
  • the so-called multi-piece double-disc structure uses the active member 11 as a transition wheel.
  • the transition wheel is a transmission gear 36, which is disposed between the two split disks 33 and is sleeved on the shaft 37.
  • the shaft 37 is a passive follower 9 and serves as a connecting rod 12 of the braking member for connection.
  • the sliding pin 5 passes through the transmission gear 36, the brake pads 2, 16 and the following inner disc body braking member 35, and both ends thereof are located in the sliding holes 7 of the braking member 2 and the braking member 16, respectively. It is also possible to change the sliding hole 7 to be connected with the sliding pin 5 and set the sliding hole 7a on the transmission gear 36.
  • the spring 3 and the spring 20 are installed at both ends of the shaft 37; the action block 13 in the force conversion mechanism is a two-piece split type, which is respectively connected to both end faces of the transmission gear 36.
  • the brake members 2, 16 When the brake is relieved in Embodiment 3, if the forces of the brake springs 3a and 20a are sufficiently large, the brake members 2, 16 can be restricted from moving within a limited range, and the elastic retaining ring 39 can be set to limit them to a limited extent. The movement ensures that the concave-convex surface of the action block 13 does not cross the convex-concave surface of the driving block 14.
  • This structure can be provided without a sliding pin and a sliding hole, and the force can be directly transmitted by the action block 13 and the driving block 14.
  • the braking member 16 is not provided, and only the braking member 2 is provided.
  • Figs. 11 to 13 show a fourth embodiment of the present invention, in which the same or similar parts as those in the above embodiment are also designated by the same reference numerals.
  • This embodiment is an application example of the third embodiment to a reducer, and the corresponding connection structures are shown in Figs. 11 to 13.
  • the two side plates 32 in the fixed seat are respectively connected to the two inner walls of the reduction case.
  • the driving gear 36 is the driving member that meshes with the front gear 38 of the reducer.
  • the passive follower is the output drive shaft of the reducer. 37.
  • the connection shaft 31, the split disk 33, and the brake pad 34 in the figure are the same as those in the third embodiment, and will not be repeated here.
  • FIG. 14 shows a fifth embodiment of the present invention, in which the same or similar components as those in the above embodiment are designated by the same reference numerals.
  • the friction surfaces of the braking member 2 and the fixing base 1 are both tapered surfaces.
  • the fixing seat 1 is directly fixed on the follower housing 40, and the braking member 2 with a tapered friction surface includes a tapered disc body 21 and a core body 22, which use the same compensation mechanism as in Embodiment 2, namely, an improved ring gear A structure (not shown), one end of the connecting rod 12 is coupled to an inner fixing plate 41, and a bearing 42 is installed between the force conversion mechanism 4 and the inner fixing plate 41 to reduce the friction of the force conversion mechanism.
  • the remaining components include a driving member 11, a driven member 9, a sliding pin 5, and a spring 3, which are not described again.
  • Fig. 15 shows a sixth embodiment of the present invention, in which the same or similar parts as those in the above embodiment are shown with the same reference numerals.
  • the gravity of the driving member 11 and the driven member 9 (referring to the vertical arrangement of the driving member on top) is used as the force for limiting the limited displacement of the force conversion mechanism 4 and the braking force, and no connecting rod is required .
  • the fixed seat also doubles as a connecting structural member of the upper driving member housing 43 and the lower driven member housing 44.
  • a bearing 42 is installed between the force conversion mechanism 4 and the thrust plate 45, and a bearing 46 is installed between the driving member and the driven member.
  • the braking member 2 also includes a disc body 21 and a core body 22, and the aforementioned compensation mechanism may be adopted between the disc body 21 and the core body 22, or a key 47 and a spring 48 may be directly fitted with threads.
  • a screw 49 is provided at the position of the key of the disk body 21, and when the friction member is worn, the screw 47 is pushed to the rotatable position with the screw 49 to adjust the friction gap.
  • 16 to 18 show a seventh embodiment of the present invention.
  • components that perform the same or similar functions as those in the above-mentioned embodiment are marked with the same reference numerals.
  • the structure of this embodiment is different from that of the above embodiment, in which the force conversion mechanism converts the main power into a radial force to release the brake against the braking force of the spring.
  • the fixing base 1 may be fixed on the follower housing, or may be fixed at other positions.
  • the inner wall of the fixing seat 1 functions as a brake pad, which is marked as 6a in the figure.
  • the cylindrical surface on the braking block 6a is a braking friction surface, which is called a braking cylindrical surface 50.
  • the braking member is in the form of a shoe block 2a and is hinged on the driven member 9 by a support pin 51.
  • the action of the action block 13a in the radial force conversion mechanism 4a is performed by the front end of the slide pin 5a.
  • the active surface of the driving block 14a is the mating surface 53 and is directly fixedly mounted on the shoe block 2a.
  • the driving block 14a and the shoe block 2a can also be integrated, which is the case in this embodiment.
  • a rolling member 52 is provided at the front end thereof.
  • the radial force conversion mechanism 4a should preferably be arranged in a uniform manner relative to the center of movement of the moving body. This embodiment uses two symmetrical arrangements. When the main member 11 receives the main power, the cleaning pin 5a is driven to move, and the rolling member 52 on the pressing member 5 presses the mating surface 53 (see FIG.
  • FIG. 19 shows an eighth embodiment of the present invention, in which the driving member drives the driven member to perform linear motion (that is, axial movement in the left-right direction in the figure).
  • the braking member 2 and the driving block 14 are integrally connected.
  • the two braking members 2 are respectively located in the notches of the two plates of the driven member 9, and the action block 13 is located between the braking member 2 and the driving block 14.
  • the inclined surface on the driving block 14 matches the inclined surface on the action block 13.
  • the two ends of the spring 3 are connected to the inner end of the driving block 14, respectively, and the friction plate on the outer side of the brake member 2 is fixed.
  • the braking friction surface on the seat 1 is clutched.
  • the driving block 14 compresses the spring 3 and moves inward, so that the braking member 2 and the braking friction surface are disengaged.
  • the brake is released and the follower 9 moves with the master 11.
  • the spring 3 acts to connect the integral acting block 13 and the braking member 2 from the inside to the outside.
  • the braking member 2 contacts the braking friction surface to realize the braking of the driven member 9.
  • the brake of the present invention is provided with a force conversion mechanism in various corresponding structures as described in the embodiments.
  • the main force of the driving member is used to overcome the braking force to release the braking state, so that the passive follower and the driving member maintain normal operation.
  • the brake of the present invention has significant substantive features. It does not need to be provided with an additional force source device, and has a simple structure. In the normal running process, it saves energy, has reliable braking, and has a wide range of applications. Especially when it is used in mining machinery with explosion-proof requirements, it does not require additional explosion-proof measures because it does not require additional force sources (such as electromagnets), and the work is completely safe and reliable.
  • the brake of the present invention will have broad application prospects in mining, metallurgy, lifting, construction and general mechanical devices.

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Description

常闭制动器 技术领域
本发明涉及一种用于制动运动物体的机械式常闭制动装置。 这里所谓常闭式制动 装置是指，当主动件与从动件处于静止状态吋，该制动装置始终处于制动状态。
背景技术
已有的制动器，无论是机械动力式或电磁式，或者是电磁液压式，均需要结构较 复杂的、消耗相当能源的力源装置。 如现有的常闭式制动器，其需要附加的力源装置 提供外力来解除常闭式制动。 另以电磁抱闸式制动器为例，常闭状态是以弹簧力作为 制动力来对物体进行制动的，当该物体需要运行或转动时，则需向电磁铁通电，以产 生电磁力克服弹簧力来解除常闭的制动状态。
中国发明专利公报 1989年 4月 26日公开了申请号为 87102097，题为 "以惯性力转 换为制动力的制动装置"。 该制动装置由附加力源装置、随动机构、制动机构和增力 机构构成，实现制动时的主要制动外力是由被制动物体在运动时所具有的惯性力转换 而来的。 这种装置具有制动时间短，缓解速度快，工作可靠的特点，但正常运动状态 仍需要附加力源装置来提供制动操作力，而附加力源装置工作时，仍需要消耗一定的 能源。
有鉴于此，本发明是对包括上述专利的现有技术进一步发展和重大改进而提出一 种结构紧凑，在正常的运转状态或静止状态时不需要额外的力源即可实现制动或解除 制动的装置。
本发明的再一目的在于，提出一种利用主动件与从动件之间在开始传动和停止传 动开始后的一段时间内出现的相对运动来实现制动或缓解制动的装置。
本发明的进一步目的在于，提出一种利用主动件与从动件之间的连接机构的凹凸 配合面来实现制动或缓解制动的装置。
发明内容
本发明提出这样一种常闭制动器，包括有主动件、从动件、可使主动件带动从动 件沿第一方向运动的连接机构、带有摩擦面的固定座，以及连接在从动件上可与固定 座上的摩擦面贴合或脱开从而实现对从动件沿第一方向运动的制动或缓解的制动件； 本发明点在于，所述连接机构设置在所述主动件和从动件之间，并包括一个可与主动 件共同进行第一方向运动的作用块，和一个可与从动件共同进行第一方向运动又可相 对于该从动件产生第二方向相对位移的驱动块；
所述作用块与驱动块具有可相对运动的配合结构，当主动件获得主动力或失去主 动力时，它们可产生这种相对运动，使驱动块相对于从动件在第二方向上产生位移, 从而实现对从动件制动的缓解或者实现对从动件的制动；
所述连接机构还包括一个限定机构，用于限定作用块和驱动块的相対运动距离， 并当制动或缓解完成后使它们处于共同的运动状态。
而且，在所述的制动器中，所述第一方向的运动可为旋转运动。
而且，在所述的制动器中，所述限定机构可包括将驱动块压向作用块的弹簧，以 保证作用块与驱动块在相对运动后，彼此之间产生足够的能够进行共同运动的力。
而且，在所述的制动器中，所述限定机构还可包括:所述主动件上连接一个盘形 件，该盘形件的中心之外设有多个销轴；还包括所述从动件上的一个盘形件，对应于 所述销轴的位置，在该从动件的盘形件上设有多个沿圆弧方向的长孔，所述销轴可在 该长孔内相对运动并抵靠该长孔的某一端。
而且，在所述的制动器中，所述主动件与从动件可以为上下设置，所述限定机构 包括在所述主动件上连接的一个盘形件，该盘形件的中心之外设有多个销轴；还包括 在所述从动件上的一个盘形件，对应于所述销轴的位置在该从动件的盘形件上设有多 个沿圆弧方向的长孔，所述销轴可在长孔内运动并最终与该长孔的某一端相抵靠。
而且，在所述的制动器中，所述作用块与驱动块的作用面之间产生相对运动的配 合结构是凸轮配合结构，而且所述作用块的作用面与驱动块的作用面中的任意一面为 凸轮面。 当它们之间发生相对转动后，可使所述驱动块产生相对所述作用块的沿第二 方向的位移，从而实现制动或使制动缓解。
而且，在所述的制动器中，所述作用块与所述驱动块的作用面可以均为凸轮面。 而且，在所述的制动器中，所述驱动块所作的第二方向的位移可以为沿旋转从动 件的轴向方向，也就是说，该制动器中具有沿旋转从动件的轴向方向产生第二方向位 移的驱动块。
而且，在所述的制动器中，所述驱动块所作的第二方向的位移可以为沿旋转从动 件的径向方向，也就是说，该制动器中具有沿旋转从动件的径向方向产生第二方向位 移的驱动块。
而且，在所述的制动器中，所述制动件与所述从动件的盘形件可以为一体结构， 而且所述制动件和盘形件的一体结构包括一个具有内齿圈的盘体和芯体，所述盘体与 所述芯体之间，可设补偿机构和可使盘体与芯体共同沿第一方向运动的滑键，所述补 偿机构包括位于芯体边缘部分的凹槽、位于该凹糟中带有齿的并可与所述盘体配合的 齿块，以及位于所述齿块与所述凹槽的底部之间的弹簧。
而且，在所述的制动器中，所述作用块的沿旋转从动件轴线的两个端面上均可以 具有凹凸作用面，并同时利用所述两个端面同时与两个驱动块配合；也就是说，该制 动器中具有沿旋转从动件轴向方向的两个端面是分别与两个驱动块配合的配合结构的 作用块。
而且，在所述的制动器中，所述固定座上的摩擦面可以为锥面、平面或柱面，所 述制动件上的制动面亦为锥面、平面或柱面。
而且，在所述的制动器中，所述第一方向的运 也可为直线运动；而且在所述的 制动器中，所述驱动块所作的第二方向的位移可以 沿直线运动从动件的垂直方向； 也就是说，该制动器中具有沿直线运动从动件的垂; i方向产生第二方向位移的驱动块。
本发明的以上构思方案和其它目的及优点，通 a以下结合附图对实施例的说明将 变得更加清晰。
附图说日月
图 1为沿图 2中的 A- A线的本发明第 1个实施例的剖视图，示出了滑动销、滑动孔及 连接杆的结构；
图 2为沿图 1中的 B-B线的剖视图；
图 3为力转换机构的轴向视图；
图 4为沿图 3中的 G- G线的剖视图；
图 5为作用块及驱动块的凹凸配合面的展开图；
图 6为沿图 7中的 C-C线的本发明第 2个实施例的剖视图；
图 7为沿图 6中的 D- D线的剖视图；
图 8为沿图 6中的 E- E线的补偿机构剖视图； 图 9为沿图 6中 F- F 的补偿机构剖视图；
图 10为本发明第 3个实施例的轴向剖视图；
图 11为本发明应用于减速机的俯视图；
图 12为沿图 11中的 M- M线的剖视图；
图 13为沿图 11中的 N- N线的剖视图；
图 14为本发明第 5个实施例的轴向剖视图；
图 15为本发明第 6个实施例的轴向剖视图；
图 16为本发明第 7个实施例的剖视图；
图 17为沿图 16中的 K-K线的剖视图；
图 18为沿图 16中的 6H-H线的剖视图；
图 19为本发明的第 8个实施例。
图 1至图 5示出了本发明的第 1个实施例。
本发 的最佳实施方式
根据本发明实施例 1的常闭制动器包含有固定座 1、制动件 2、制动弹簧 3、力转换 机构 4、从动件 9、主动件 11，其结构及相互连接关系如下：
固定座 1上设有制动块 6(二者为一体），制动件 2的制动摩擦面 8可以是平面或锥面， 与制动块 6上的摩擦面离合从而实现制动或缓解制动。 图 2所示为制动件摩擦面与制动 块 6的摩擦面紧接触的状态，即处于制动状态。
制动件 2上具有沿圆弧方向的滑动孔 7和用于连接被动的从动件 9的轴套 10，该滑 动孔 7沿圆弧方向具有一定的长度。 由于制动件 2与轴套 10成一体，所以当制动件 2与 制动块 6紧接触而处于制动状态时，是以轴套 10来实现对被动的从动件 9的制动的，而 且通过轴套 10与从动件 9的配合，制动件 2可相对从动件 9沿轴线方向滑动。
连接杆 12—端装在制动件 2上，弹簧 3装在连接杆的该端部，其弹簧力作用于制动 件 2上。 当本制动器处于制动状态时，制动件 2由于弹簧 3的作用而紧接触制动块 6。（ 图 1中制动块 16和弹簧 20的作用见后述）。
力转换机构 4由和主动件 11连接的作用块 13以及和制动件 2固定连接的驱动块 14构 成（见图 3至图 5)。 作用块 13与驱劝块 14的接触面为凸凹相配合的接触面 15(相当于凸 轮机构中的从动件上亦具有凸轮面）。 当主动件得到主动力带动作用块 13转动时，其 上的凸面段朝向驱动块 14上的凸面段移动而对驱动块 14产生推力，使驱动块 14沿轴向 移动（如图 5中箭头所示），从而驱动制动件 2克服弹簧 3的作用力外移，使制动件 2上的 制动摩擦面离开制动块 6而解除制动状态。
滑动销 5位于制动件 2的滑动孔 7内，一端与主动件 11连接，另一端与力转换机构 4 中的作用块 13配合（见图 1)。 滑动销 5可在滑动孔 7内相对移动。 利用滑动销 5在滑动孔 7内产生的位移带动作用块 13转动，即可通过驱动块 14来驱动制动件 2移动。
本发明解除常闭制动状态、使被动的从动件 9正常运动的过程是这样的：当主动件
11由诸如电动机等主动元件起动开始运转时，主动件 11获主动力随之开始转动并带动 滑动销 5在滑动孔 7内产生位移，滑动销 5另一端则带动力转换机构中的作用块 13转动， 作用块 13即对驱动块 14产生推力，利用驱动块 14使制动件 2外移而逐步解除制动，当 制动状态尚末完全解除时，被动的从动件 9仍处于静止状态。 当滑动销 5位移至滑动孔 7的一端时，制动状态被完全解除。 此时，滑动销 5则作为扭矩传递轴带动制动件 2转 动，连接在制动件轴套 10内的被动从动件 9即随之正常运动。 具体地说是，利用主动 件 11首先转动和从动件 9暂处静态的时间差，通过滑动销 5在滑动孔 7内的位移，带动 作用块 .13转动，使驱动块 14驱动制动件 2外移而解除制动状态。 当制动状态被完全解 除后，被动的从动件正常运转时，力转换机构中的作用块 13由于滑动销 5的作用而转 动，并且由于滑动孔 7的限位作用，保证作用块 13上的凸面段可靠地与驱动块 14上的 凸面段接触，使制动保持被解除的状态。
恢复常闭制动状态的过程是，当需要制动时，切断主动元件（如电动机）的电源， 主动件 11由于失去主动力因相对于运行时的反扭矩而降速，滑动销 5即在滑动孔 7内产 生与起动时相反方向的位移，从而带动作用块 13相应反转，使作用块 13上的凸面段朝 驱动块 14上的凹面段移动，直至作用块 13相对于驱动块 14的推力消除。 由于制动弹簧 3作用于制动件 2，所以制动件 2由于弹簧 3的压力接触制动块 6，产生摩擦阻力使制动 件 2停止运动，连接在制动件 2和轴套 10内的被动的从动件 9随之被制动，即实现制动 状态。
需要指出的是，上述描述中仅涉及了作用块 13的一个轴向侧面作为作用面与驱动 块 14的凸轮作用面配合的情形，伹图 1至图 5中所示出的实际上是一个作用块 13与两个 驱动块 14和 18配合的结构（见图 5中作用块 13下面的部分），该结构中不伹具有制动件 2， 还具有另一个制动件 16。 实际上本实施例中可以不设置制动件 16,从上面描述可以知 道，一般情况下一个制动件 2的作用就足够，制动件 16的位置上可换成一块简单的板 件，而连接杆 12的另一端可连接在这板件上。 以下本发明的第 2个实施例将对带有制 动件 16的结构进行详细描述。（图 4中表示了另一驱动块 18和接触面 19以及制动弹簧 20， 见后述）
还需要指出的是，本实施例的从动件与主动件的相互连结关系实际上相当于一个 弹性联轴器。
图 6至图 9示出本发明的第 2个实施例，其中与上述实施例中相同或相类似的部件 用相同的标号标出。
在制动块 6的另一侧设置与制动件 2相对应的制动件 16，制动件 16的制动摩擦面相 应于制动块 6的另一侧面摩擦面离合。 作用块 13的另一端设置与驱动块 14相对应的驱 动块 18(参见图 4、图 5)，作用块 13与驱动块 18的凸、凹接触面 19与接触面 15对称。 制 动件 16的轴套与制动件 2的轴套之间设置有可使该两件同时运动和同时停止的滑键 17， 而且该两制动件可沿滑键 17沿轴向相对移动。 连接杆 12的两端部分别连接在制动件 2 和制动件 16上，连接在制动件 2上的连接杆 12的端部装有弹簧 3，该弹簧的弹力作用于 制动件 2。 连接杆 12的另一端部可装有与弹簧 3相对称的弹簧 20(参见图 2) ,该弹簧的 弹簧力作用于制动件 16上。 此外，连接杆 12的另一端也可固定在制动件 16上，弹簧 3 通过连接杆 12作用在制动件 16上（见图 7)。 制动件 2和制动件 16的制动摩擦面上设置有 摩擦片，为使受力均勾，滑动销 5和与之相应的滑动孔 7至少设置两个，且对称均匀分 布，本实施例制动件 2上的滑动孔 7为 6个（见图 6)，相对应的滑动销 5为 6根，为使受力 均匀，用于连接制动件的连接杆 12至少设两根，且为对称均匀设置；本实施例的制动 弹簧 3为两根，制动弹簧 20可为两根，也可不设。
本发明第二个实施例解除制动状态的工作过程是，作用块 13随滑动销 5在主动件 获主动力起动时的转动而转动，对两端的驱动块 14和驱动块 18产生向外的推力，使制 动件 2和制动件 16同时向外移动而离开制动块 6，实现常闭制动的解除，使被动的从动 件正常运转。 主动件失去主动力时，作用块 13随滑动销 5向相反方向转动，使作用块 上的凸面段朝驱动块的凹面段移动，推力消除，制动弹簧 3和制动弹簧 20分别作用于 制动件 2和制动件 16上，或由制动弹簧 3通过连接杆 12同时作用于制动件 2和制动件 16 上，使两制动件同时向内移动而紧接触制动块 6，恢复常闭制动状态。
在实施例 2中，制动件 2和制动件 16均还可由带有内齿的盘体 21和芯体 22构成，盘 体 21与芯体 22之间设有制动补偿机构 23和可使盘体与芯体同时运转或停止的滑键 24， 该滑键 24还用于确保盘体沿芯体安装结构的平衡。 在本实施例中，制动件 2与制动件 16上的制动补偿机构是对称设置的。 制动块 6为双片结构，由支撑轴 30可滑动地联接， 另外，在双片式制动块 6的中间，连接杆 12上还设有一个中间内盘体 29，用于增加制 动时的摩擦力。 本制动补偿机构为改进的齿圈式结构，即：盘体 21的内圈上设有齿圈 26,芯体 22的圆周上设置齿块 25(见图 8、图 9)，该齿块 25上有与齿圈 26相配合的外齿， 每个齿的外侧为斜面，内侧为垂直于传动轴线的垂直面。 所述齿圈 26和齿块 25可以是 螺纹面配合，滑键 24的底部设置弹簧 28，可用螺钉调动滑键 24，使盘体 21与芯体 22可 以沿螺纹旋转，作为人工调节摩擦间隙。 齿块 25装在芯体 22沿圆周方向形成的凹槽 27 内，凹槽 27的底部设有作用于齿块 25的弹簧 27a (见图 8)。 齿块 25成对设置，本例为四 对共八块，其中部分成对均匀布置的（本例为四块，图 6中未涂黑的）为完全接触（见图 8)。 另外成对均匀布置的（图 6中涂黑的四块）为部分接触（见图 9)。 完全接触的为工作 状态.即当制动件的芯体被力转换机构驱动而外移时，带动盘体外移而解除制动。 当 力转换机构的推力解除时，制动弹簧作用于芯体，使盘体与制动块 6紧接触而实现制 动。 齿为部分接触的齿块 25处在补偿状态，当盘体上的摩擦片被一定程度的磨损后， 芯体 22在驱动块作用下，向外移动时与盘体 21产生相对运动，齿块 25克服弹簧 27a的 作用力在凹糟内下移，而其上的齿滑入盘体的下一齿圈上，即处于完全接触，变为工 作状态，而原为完全接触的齿块则变为部分接触的补偿状态。
这里要强调说明的是，本实施例 2中所述补偿机构 23，按其原理可以在本发明制 动件为盘式的其他制动器中使用，如后述实施例 3、 4、 5、 6等。
图 10示出了本发明的实施例 3。 同样，其中与上述实施例中相同或相类似的部件 用相同的标号标出。
图 10为本实施例沿轴线方向的剖视结构图。 本实施例是在上述实施例的基础上的 一种变型。 其中的固定座是由三根连接轴 31和与这三轴两端连接的两个侧板 32构成。 制动块 6由两个分体式盘 33组成，均固定在连接轴 31上，制动件 2和制动件 16则分别与 制动块 6的两分体式盘 33对应。 制动件 2和制动件 16与两个分体式盘 33之间可设制动块 34和随动内盘体制动件 35，制动块 34连接在连接轴 31上，并可沿该轴移动；在制动块 34的侧面设置与之同轴线的随动内盘体制动件 35，制动件、制动块及随动内盘体制动 件的摩擦面相互对应离合。 如此所谓的多片式双盘结构，以主动件 11作为过渡轮。 在 本实施例中，过渡轮为传动齿轮 36，设置在两分体式盘 33之间，并套装在轴 37上。 轴 37即为被动的从动件 9,又作为制动件的连接杆 12起连接作用。 滑动销 5穿过传动齿轮 36、制动块 2、16和随动内盘体制动件 35，其两端分别位于制动件 2和制动件 16的滑动 孔 7内。 也可将滑动孔 7改为与滑动销 5的连接配合，将滑动孔 7a设在传动齿轮 36上。 弹簧 3和弹簧 20装在轴 37的两端；力转换机构中的作用块 13为两块分体式，分别连接 在传动齿轮 36的两端面上。 当驱动块 14和驱动块 18分别对制动件 2和制动件 16产生驱 动推力时，两制动件 2和 16分别克服制动弹簧 3a和 20a的作用力而外移，使制动块 34、 随动内盘体制动件 35处于无压力的松动状态而被解除制动。 当驱动块 14和 18的推力消 除时，来自两制动弹簧的作用，制动件 2和 16对随动内盘体制动件 35、制动块 34产生 压力，使之向内移动，直至相互紧接触而实现制动。
实施例 3制动器缓解时，若制动弹簧 3a和 20a的作用力足够大，即可限制制动件 2、 16在有限范围内移动，也可以通过设置弹性挡圈 39限位，使它们有限地移动，保证使 作用块 13的凹凸面不致越过驱动块 14的凸凹面。 此种结构可以不设滑动销和滑动孔， 由作用块 13和驱动块 14直接进行力传递。 也可如实施例 1所述一样，不设制动件 16， 只有制动件 2。
图 11-图 13示出本发明的第 4个实施例，其中与上述实施例中相同或相类似的部件 也用相同的标号标示出。
本实施例是实施例 3在减速机上的应用实例，相应的连接结构见图 11至图 13。 在 这里，固定座中的两侧板 32分别与减速机箱体的两内壁连接，传动齿轮 36即主动件与 减速机的前级传动齿轮 38啮合，被动的从动件是减速机的输出传动轴 37。 关于图中的 连接轴 31、分体式盘 33和制动块 34和实施例 3相同，这里不再重复。
图 14示出本发明的第 5个实施例，其中与上述实施例中相同或相类似的部件用相 同的标号标示出。 在实施例 5中，制动件 2与固定座 1的摩擦面均为锥面。
固定座 1直接固定在从动件外壳 40上，带锥面摩擦面的制动件 2包括锥形盘体 21和 芯体 22，它们采用与实施例 2同样的补偿机构，即改进的齿圈式结构（图中未示出）， 连接杆 12的一端联接在一个内固定板 41上，力转换机构 4与内固定板 41中间装有一轴 承 42以减小力转换机构的摩擦力。 其余构件还有主动件 11、从动件 9、滑动销 5和弹簧 3不再赘述。
图 15示出了本发明的第 6个实施例，其中与上述实施例中相同或相类似的部件以 相同的标号示出。
在本实施例中，利用主动件 11、从动件 9的重力（指主动件在上的竖向设置）作为 限定力转换机构 4有限位移的作用力和制动作用力，并且不需要连接杆。 固定座兼作 上主动件外壳 43与下从动件外壳 44的联结构件，力转换机构 4与推力板 45之间装有轴 承 42,同时在主动件、从动件之间装有一轴承 46，以减小摩擦力。 制动件 2也包括盘 体 21与芯体 22，盘体 21与芯体 22之间可采用前述补偿机构，也可以直接用螺纹配合并 设有键 47和弹簧 48。 盘体 21的键糟位置上设有螺钉 49，当摩擦件摩损后，用螺钉 49将 键 47顶到可旋动的位置，即可调节摩擦间隙。
图 16-图 18示出了本发明的第 7个实施例。 在该实施例中，与上述实施例中的部件 作用相同或相类似的部件用相同的标号标出。
本实施例与上述实施例的结构有差异，其中力转换机构是将主动力转换成径向力 克服弹簧的制动作用力而解除制动的。 固定座 1可固定在从动件外壳上，也可固定在 其他位置上。 固定座 1的内壁起制动块的作用，图中标注为 6a。 制动块 6a上的圆柱面 为制动摩擦面，称为制动圆柱面 50,制动件的形式为蹄块 2a并由支撑销 51铰接在从动 件 9上。 径向力转换机构 4a中的作用块 13a的作用由滑动销 5a的前端充当。 驱动块 14a 的作用面在这里是配合面 53并直接固定安装在蹄块 2a上，驱动块 14a与蹄块 2a也可为 一体，本实施例即如此。 为了减小滑动销 5a的驱动摩擦，其前端设有滚动件 52。 为了 使主动件 11、从动件 9之间不产生径向分力，径向力转换机构 4a应以相对于运动体的 运动圆心均勾布置为佳。 本实施例采用两件对称布置。 当主动件 11得主动力后，带动 清动销 5a移动，其上的滚动件 52压迫配合面 53(见图 16)，产生向下的径向分力克服弹 簧 3a的作用力，使制动蹄块 2a沿径向向内移动，使制动柱面 50的制动缓解，主动件 11、 从动件 9正常运转。 当主动件 11失去主动力后，滑动销 5a相对配合面 53产生相反方向 的运动，在弹簧 3a的作用力的作用下恢复制动状态。
图 19示出了本发明第 8个实施例，其中的主动件带动从动件作直线运动（即图中左 右方向的轴向运动）。
如图 19所示，制动件 2与驱动块 14连接成整体，两制动件 2分别位于从动件 9的两 侧板的槽口内，作用块 13位于制动件 2和驱动块 14之间的凹槽内，驱动块 14上的斜面 与作用块 13上的斜面相配合，弹簧 3的两端分别与驱动块 14的内端连接，制动件 2外侧 边上的摩擦片与固定座 1上的制动摩擦面离合。 当主动件 11得主动力后作直线运动， 由于作用块 13的斜面作用，使驱动块 14压缩弹簧 3而内移，使制动件 2与制动摩擦面脱 离，从而使对从动件 9的制动解除，从动件 9随主动件 11运动。 当主动件失去主动力时， 弹簧 3作用，连接成整体的作用块 13和制动件 2由内向外移动，制动件 2接触制动摩擦 面，实现对从动件 9的制动。
本发明制动器在如实施例所述各种相应的结构中设置了力转换机构，利用主动件 的主动力克服制动作用力解除制动状态，使被动的从动件与主动件保持正常运转。
与已有技术相比，本发明制动器有显著的实质性特点，它无需设置附加力源装置， 并且结构简单，在正常运转过程中，节省能源，制动可靠，适用范围十分广泛。 特别 是当其应用于有防爆要求的矿山机械装置中时，由于不需要额外的力源（如电磁铁等）， 也就不需再加防爆措施，工作是完全安全可靠的。
本发明制动器在矿山、冶金、起重、建筑及一般机械装置中将有广泛的应用前景。

Claims

权利要求
1、一种常闭制动器，包括有主动件、从动件、可使主动件带动从动件沿第一方 向运动的连接机构、带有摩擦面的固定座以及连接在从动件上可与固定座上的摩擦面 贴合或脱开从而实现对从动件沿第一方向运动的制动或缓解的制动件；其特征在于， 所述连接机构设置在所述主动件和从动件之间，并包括一个可与主动件共同进行 第一方向运动的作用块，和一个可与从动件共同进行第一方向的运动又可相对于该从 动件产生第二方向的相对位移的驱动块；
所述作用块与驱动块具有当主动件获得主动力或失去主动力时、可在第二方向上 产生相对运动的配合结构；
所述连接机构还包括一个用于限定作用块和驱动块的相对运动距离的限定机构。
2、如权利要求 1所述的制动器，其特征在于所述限定机构包括将驱动块压向作用 块的弹簧。
3、如权利要求 1、2所述的制动器，其特征在于所述限定机构包括所述主动件上 连接一个盘形件，该盘形件的中心之外设有多个销轴；所述从动件上的一个盘形件对 应于所述销轴的位置，设有多个沿圆弧方向的长孔。
4、如权利要求 2、3所述的制动器，其特征在于所述作用块与驱动块的作用面之 间产生相对运动的配合结构是凸轮配合结构，而且所述作用块的作用面和所述驱动块 的作用面中的任意一面为凸轮面。
5、如权利要求 4所述的制动器，其特征在于所述作用块与驱动块的作用面均为凸 轮面。
6、如权利要求 4、5所述的制动器，其特征在于具有沿旋转从动件的轴向方向产 生第二方向位移的驱动块。
7、如权利要求 4、5所述的制动器，其特征在于具有沿旋转从动件的径向方向产 生第二方向位移的驱动块。
8、如权利要求 4、5所述的制动器，其特征在于具有沿直线运动从动件的垂直方 向产生第二方向位移的驱动块。
9、如权利要求 6所述的制动器，其特征在于具有沿旋转从动件轴向方向的两个端 面是分别与两个驱动块配合的配合结构的作用块。
10、如权利要求 6所述的制动器，其特征在于所述一个驱动块对应一个盘形制动 件，而且所述盘形制动件的制动面为锥面或平面。
11、如权利要求 6所述的制动器，其特征在于所述驱动块为两块，分别对应两个 盘形制动件，而且所述盘形制动件的制动摩擦面为锥面或平面。
12、如权利要求 11所述的制动器，其特征在于两盘形制动件之间设有内盘体。
13、如权利要求 10、11、12所述的制动器，其特征在于盘形制动件与分体式盘对 应，所述主动件为过渡轮。
14、如权利要求 10所述的制动器，其特征在于制动器设在减速器的内部，所述主 动件为过渡齿轮，所述从动件为减速器的输出轴。
15、如权利要求 11、12所述的制动器，其特征在于制动器设在减速器的内部，所 述主动件为过渡齿轮，所述从动件为减速器的输出轴。
16、如权利要求 6、10所述的制动器，其特征在于所述主动件与从动件为上下设 置。
17、如权利要求 6、 9、 10、 11、 12、 13、 14、 15、 16中任意一项所述的制动器， 其特征在于所述制动件与所述从动件的盘形件为一体结构，而且所述制动件和盘形件 的一体结构包括一个具有内齿圈的盘体和芯体，所述盘体与所述芯体之间设有补偿机 构和可使盘体与芯体共同沿第一方向运动的滑键，所述补偿机构包括位于芯体边缘的 凹槽、位于该凹槽中带有齿的并可与所述盘体配合的齿块，以及位于所述齿块与所述 凹槽的底部之间的弹簧。
18、如权利要求 7所述的制动器，其特征在于所述驱动块均匀布置，所述作用块 由滑动销轴的前端充当并设有滚动件。
PCT/CN1995/000055 1994-07-02 1995-06-30 Frein normalement serre WO1996001380A1 (fr)

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US08/765,994 A-371-Of-International US6374963B1 (en) 1994-07-02 1995-06-30 Normally closed brake
US09/994,570 Division US6588552B2 (en) 1994-07-02 2001-11-27 Brake

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WO1996001380A1 true WO1996001380A1 (fr) 1996-01-18

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PCT/CN1995/000055 WO1996001380A1 (fr) 1994-07-02 1995-06-30 Frein normalement serre

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EP (2) EP0769634B1 (zh)
JP (1) JP3959109B2 (zh)
KR (1) KR100297569B1 (zh)
CN (1) CN1099464A (zh)
AT (2) ATE273464T1 (zh)
AU (1) AU697266B2 (zh)
BG (1) BG62372B1 (zh)
BR (1) BR9508214A (zh)
CA (1) CA2194285C (zh)
DE (2) DE69531687T2 (zh)
FI (1) FI115792B (zh)
HU (1) HU220502B1 (zh)
NO (1) NO327166B1 (zh)
OA (1) OA10393A (zh)
PL (1) PL176385B1 (zh)
RU (1) RU2188346C2 (zh)
UA (1) UA44895C2 (zh)
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WO2004046576A1 (fr) * 2002-11-16 2004-06-03 Xingyun Xie Unite de couplage d'arbre

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DE20302402U1 (de) * 2003-02-13 2004-06-24 Dewert Antriebs- Und Systemtechnik Gmbh & Co. Kg Drehmomentreduzierte Brems- und Kupplungsanordnung
EP1679451A1 (fr) * 2005-01-07 2006-07-12 Somfy SAS Frein, mécanisme de manoeuvre incorporant un tel frein et installation de fermeture, de protection solaire ou de projection d'images comprenant un tel mécanisme
EP1974296B8 (en) * 2005-12-19 2016-09-21 Commvault Systems, Inc. Systems and methods for performing data replication
PL2212580T3 (pl) * 2007-11-27 2012-11-30 Asteria Performance Inc Pierścieniowy hamulec tarczowy i sposób zwiększenia siły docisku klocków hamulcowych
IT1392302B1 (it) * 2008-12-18 2012-02-24 Peruzzo S R L Dispositivo di innesto e disinnesto per una trasmissione di potenza, particolarmente per attrezzature e macchine agricole
CN102042353B (zh) * 2009-10-20 2013-08-28 长沙三占惯性制动有限公司 轴用制动装置
CN110617288A (zh) * 2019-10-24 2019-12-27 泰尔重工股份有限公司 一种带制动轮弹性联轴器
US20210395055A1 (en) * 2020-06-17 2021-12-23 Forcome Co. Ltd. Systems for a braking assembly in a gear housing
CN112228475B (zh) * 2020-09-04 2022-07-05 国网河南省电力公司柘城县供电公司 一种电力液压制动器

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US2783861A (en) * 1954-11-29 1957-03-05 Cleveland Pneumatic Tool Co Drive-released brake
US2838150A (en) * 1954-10-29 1958-06-10 Ind Clutch Corp Interconnected clutch and brake mechanism

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US1855057A (en) * 1930-11-19 1932-04-19 Karsten Fred Automatic automobile brake
US2573939A (en) * 1949-10-24 1951-11-06 Gear Grinding Mach Co Automatic locking means for rotary driven members
DE833363C (de) * 1950-12-15 1952-03-06 Einar Troeften Bremssicherung bei Gefaellebahnwagen mit Zugseilantrieb
US3688877A (en) * 1970-11-04 1972-09-05 Horton Mfg Co Inc Device for releasing a spring urged brake
US3994376A (en) * 1973-04-25 1976-11-30 International Harvester Company Self actuating mechanism for braking a driven member upon discontinuating of drive thereto
US4122926A (en) * 1976-12-02 1978-10-31 Gulf & Western Manufacturing Company Fluid operated clutch and brake
US4135611A (en) * 1977-01-14 1979-01-23 Gulf & Western Manufacturing Company Press drive clutch with brake
US4186827A (en) * 1978-06-22 1980-02-05 Gulf & Western Manufacturing Company Fluid operated clutch and brake
US4785926A (en) * 1987-04-15 1988-11-22 Industrial Clutch Corporation Clutch/brake

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US2838150A (en) * 1954-10-29 1958-06-10 Ind Clutch Corp Interconnected clutch and brake mechanism
US2783861A (en) * 1954-11-29 1957-03-05 Cleveland Pneumatic Tool Co Drive-released brake

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046576A1 (fr) * 2002-11-16 2004-06-03 Xingyun Xie Unite de couplage d'arbre
US7320392B2 (en) 2002-11-16 2008-01-22 Xingyun Xie Shaft coupling unit

Also Published As

Publication number Publication date
US6374963B1 (en) 2002-04-23
FI965288A0 (fi) 1996-12-31
RU2188346C2 (ru) 2002-08-27
AU2784495A (en) 1996-01-25
DE69533376D1 (de) 2004-09-16
CN1099464A (zh) 1995-03-01
JP3959109B2 (ja) 2007-08-15
HU220502B1 (hu) 2002-02-28
HUT78068A (hu) 1999-07-28
DE69531687D1 (de) 2003-10-09
FI965288A (fi) 1997-02-26
EP0769634A1 (en) 1997-04-23
ATE248996T1 (de) 2003-09-15
CA2194285A1 (en) 1996-01-18
US6588552B2 (en) 2003-07-08
DE69533376T2 (de) 2005-08-18
NO327166B1 (no) 2009-05-04
EP0769634B1 (en) 2003-09-03
FI115792B (fi) 2005-07-15
AU697266B2 (en) 1998-10-01
DE69531687T2 (de) 2004-07-15
KR100297569B1 (ko) 2002-04-24
US20020033308A1 (en) 2002-03-21
EP1209379A2 (en) 2002-05-29
PL318103A1 (en) 1997-05-12
HU9700002D0 (en) 1997-02-28
JPH10506171A (ja) 1998-06-16
EP1209379A3 (en) 2002-06-19
OA10393A (en) 2001-11-30
BG62372B1 (bg) 1999-09-30
CA2194285C (en) 2005-08-02
NO965600D0 (no) 1996-12-27
EP0769634A4 (en) 1998-04-15
BR9508214A (pt) 1997-10-28
BG101179A (en) 1998-01-30
ATE273464T1 (de) 2004-08-15
EP1209379B1 (en) 2004-08-11
PL176385B1 (pl) 1999-05-31
NO965600L (no) 1997-02-26
UA44895C2 (uk) 2002-03-15

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