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
  • F16D65/00—Parts or details
  • F16D65/78—Features relating to cooling
  • F16D65/84—Features relating to cooling for disc brakes
  • F16D65/853—Features relating to cooling for disc brakes with closed cooling system
• • 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
  • F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the 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
  • 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
  • F16D65/78—Features relating to cooling
  • F16D2065/784—Features relating to cooling the coolant not being in direct contact with the braking surface

Definitions

• the present disclosure relates to disc brakes. More particularly, the present disclosure relates to internally, liquid-cooled disc brakes.
• Brakes incorporating discs may be found in a variety of vehicular and industrial applications.
• liquid-cooled disc brakes may be used.
• the brake can include a wear plate that is configured to engage a rotating disc during a braking process.
• the wear plate becomes heated due to friction involved in the retarding engagement.
• a flow of coolant e.g., water
• Liquid-cooled brakes can benefit from improvements. SUMMARY OF THE DISCLOSURE
• the present disclosure provides a new and improved fluid-cooled brake assembly having an improved flow of coolant to promote the transfer of heat from components of the assembly.
• improved heat transfer from the components to the coolant is promoted by creating a turbulent flow of the coolant in the coolant flow cavity.
• the cooling effect is also improved by constructing the coolant flow cavity with at least two coolant inlet ports and two coolant outlet ports.
• coolant inlet ports which are disposed 180° apart.
• the coolant outlet ports are disposed 90° from each inlet.
• the coolant inlets lead to radially aligned coolant entry channels, which are in flow communication with each other.
• the coolant entry channels allow coolant received therein to flow in either annular direction toward an outlet.
• Each coolant outlet channel can receive coolant from both inlets. Because of the multiport arrangement there is less of a pressure drop (i.e., less resistance) to the coolant flow between the inlets and the outlets. Thus, the shared inlet arrangement enables a higher flow rate of coolant through the cavity.
• a further exemplary embodiment is directed to having staggered rows of pin projections in the coolant flow cavity.
• the pin projections can contact the overlying brake plate. Heat can be transferred from the brake plate to the pin projections and the coolant.
• the rows of pin projections can include both full and partial pin projections.
• the partial pin projections can be part of annularly extending walls that separate chambers in the coolant flow cavity.
• the ability to have greater coolant flow, combined with more effective cooling flow within the coolant flow cavity, provides greater cooling to heated braking components, such as a wear plate. Consequently, the temperature at the contact surface of a braking component can be lowered. The lower temperature enables the entire brake to run longer and more effectively.
• the arrangement provides for an improved liquid-cooled brake that can reliably provide braking, stopping, and drag force as needed for the desired braking application.
• Figure 2 is a front view of an exemplary embodiment of the coolant flow cavity.
• Figure 3 is an angled view of a coolant flow cavity that is similar to the cavity shown in Figure 2.
• Figure 6 is an enlarged sectional view of the area indicated "A" in Figure 2.
• Figure 7 is an enlarged sectional view taken along line 7-7 in Figure 2.
• Figure 8 is an enlarged view of a portion of the structure shown in Figure 7.
• Figure 9 is an enlarged angled view of a coolant channel area shown in Figure 2.
• Figure 1 illustrates a cross-section view of an exemplary embodiment of a braking system 10.
• the braking system 10 is a disc type, internally cooled unit configured to absorb and dissipate thermal loads associated with the brake applications.
• the braking system 10 may be used in industrial applications, such as, Draw works application, mooring application (such as in the oil and gas industry), dynamic braking, emergency stopping, and
• the braking system 10 includes a brake assembly 12.
• the brake assembly is operable to stop, slow down, or to provide a continuous drag force on a rotating shaft.
• the brake assembly can be used in industrial applications, including the control of wind turbine blades.
• An example of such braking control can be found in U.S. Application 61/834,646 filed June 6, 2013, which is herein incorporated by reference in its entirety.
• the hub 14 also has a splined exterior surface 16 which engages three friction discs 20, 22, 24. These friction discs rotate with the hub 14. Central splined openings in the friction discs mate with the splines on the hub allowing the friction discs to move in axial direction on the splines of the hub.
• Each of the friction discs 20, 22, 24 has friction material 26 (e.g., brake pads) attached thereto on both axial sides. These brake pads 26 can be attached to the friction discs by fasteners 28.
• the brake pads 26 can be annular or arcuate in shape.
• the brake assembly 12 includes a mounting flange 30, two reaction plates 34, 36, and a pressure plate 38.
• An annular wear plate 40 is fastened to the inner side of the mounting flange 30.
• a respective wear plate 40 is fastened to each respective side of a reaction plate 34, 36.
• Another wear plate 40 is fastened to the inner side of the pressure plate 38.
• Each wear plate 40 can be held in position by rings of bolts at interior and exterior portions of the wear plate.
• the wear plate 40 can be fastened to the mounting flange 30 by a first ring of bolts 44 attached near the interior of the mounting flange 30 and a second (outer) ring of bolts 46 attached near the exterior of the mounting flange 30.
• the braking system 10 includes a piston 54 that is operated to cause the braking action. As discussed in more detail later, movement of the piston 54 causes braking engagement to occur between the wear plates 40 and the brake pads 26. Each wear plate 40 is configured to frictionally engage a brake pad 26 during the braking process.
• the mounting flange 30 is attached to a fixed body 32.
• the mounting flange 30 can be anchored to a structure to which the brake is mounted.
• the mounting flange does not rotate.
• This fixed body prevents rotational movement of the brake assembly 12 when braking is applied.
• each of the reaction plates 34 and the pressure plate 38 do not rotate.
• the piston 54 which can be an annular piston axially movably mounted in an annular cylinder, also does not rotate.
• Each of the pressure plate 38 and the reaction plates 34, 36 include openings 62, 64 which extend on their periphery.
• the pressure plate 38 and the reaction plates 34, 36 can move in the axial direction guided by studs 60.
• compression springs 66 extend between the mounting flange 30, reaction plates 34, 36, and the pressure plate 38.
• the compression springs 66 extend in surrounding relation of the studs 60.
• the compression springs 66 are operable to separate the mounting flange 30, the reaction plates 34, and the pressure plate 38. That is, the compression springs 66 are configured to release (act against) the braking force.
• the rotating shaft rotates the hub 14, which in turn rotates each of the friction discs 20, 22, 24.
• hydraulic or pneumatic pressure is applied to one or more pressure ports 68 of the cylindrical body of the piston 54.
• the pressure applied to a cavity in the cylinder causes the piston 54 to move axially.
• the movement of the piston 54 will impart axial movement to the pressure plate 38.
• the friction discs 20, 22, 24 (and their brake pads 26) to be squeezed in sandwiched relation between the reaction plates 34 and the mounting flange 30.
• force applied by movement of the piston 54 causes the wear plates 40 to slow and/or stop the rotation of the hub 14 and the shaft that is engaged therewith.
• the clamping force applied by the brake fluid pressure causes a rotational drag force corresponding to the applied fluid pressure on the rotating disc 24.
• this drag force operates to resist rotational movement of the rotating disc 24, and thus provides braking action to the rotating disc 24.
• the braking action can be effectively varied rapidly by changing the brake fluid pressure applied at the fluid pressure port.
• multi friction disc arrangement described with regard to Figure 1 is exemplary, and in other arrangements other configurations may be used.
• less or more friction discs can be used along with less or more reaction plates.
• two friction discs may be used with one reaction plate.
• four friction discs may be used with three reaction plates, etc.
• FIG. 2 shows a portion of the brake assembly 12.
• the front view includes an exemplary embodiment of an annular coolant flow cavity 50.
• the cavity is structurally configured to cool (during braking operation) an adjacent overlying wear plate (or disc). For purposes of clarity, the cavity is shown with the wear plate removed.
• the coolant flow cavity 50 is configured to hold a heat transfer coolant (e.g., a liquid-based coolant such as water).
• a heat transfer coolant e.g., a liquid-based coolant such as water.
• Each coolant flow cavity 50 has coolant ports 52 through which fluid coolant can enter or exit.
• coolant ports 52 there are four coolant ports 52 associated with the coolant flow cavity 50.
• Two fluid inlet ports 56 (or openings) to the cavity 50 are approximately 180 apart.
• Two fluid outlet ports 58 are also approximately 180 apart.
• Each fluid outlet opening 58 is located approximately halfway between the fluid inlet openings 56. Thus, each outlet opening 58 is approximately 90° away from an inlet opening 56, and vice versa. Coolant enters the cavity 50 through an inlet opening 56, then flows through the cavity 50, and then exits the cavity 50 through an outlet opening 58.
• Coolant flowing through the respective coolant flow cavities 50 of the mounting flange 30, the reaction plates 34, and the pressure plate 38 receives heat during the heat transfer process of cooling the brake system.
• This heated coolant exits from a coolant outlet port 58 and then releases its absorbed heat to atmosphere through a radiator or to a heat sink.
• the coolant when at a lower temperature, can then be returned to a cavity inlet port 56 for reuse.
• the coolant flow cavity 50 also includes a plurality of concentric rings positioned between the inside wall 82 and the outside wall 84 that radially bound the cavity 50.
• the use of two concentric rings 86, 88 define three separate flow chambers 90, 92, 94.
• the top of each concentric ring 86, 88 also has a substantially flat top 96.
• the flat tops 96 are also substantially the same height as the flat tops 74 of the projections 70.
• the upper surfaces 96 of the rings 86, 88 can also be used to both support the inner surface of a wear plate 40 and remove heat therefrom. Coolant within the cavity 50 functions to remove heat from the rings 86, 88.
• the set of three pins in the pin row 102 in chamber 92 is offset from the set of three pins in the pin row 104 in chamber 90.
• the set of three pins in the pin row 102 is also offset from the set of three pins in the pin row 106 in chamber 94.
• the exemplary manifold structure provides for directing the desired percentages of incoming coolant into the different flow chambers 90, 92, 94 of the coolant jacket 50. That is, the exemplary arrangement allows to be provided to each respective area 90, 92, 94, the predetermined amount of coolant allocated for that respective area.
• the exemplary water cooling configuration allows for liquid- cooled brakes that can operate for extended periods of the time while resisting high horse power and torque loads.
• the cooling also facilitates being able to operate the brake in a continuous drag mode, which continuous drag may be required in various types of applications to control the speed and/or torque of a rotating shaft.
• the embodiments of the liquid cooled brake achieve desirable properties, eliminate difficulties encountered in the use of prior devices and systems, solve problems and attain the desirable results described herein.
• At least one of a, b or c (Example 1) means “at least one of a, b and/or c.”
• language which refers to a list of items such as “at least one of a, b and c" (Example 2) means “at least one of a, b and/or c.”
• the list of items in Example 2 is not required to include one of each item.
• the lists of items in both Examples 1 and 2 can mean "only one item from the list of any combination of items in the list.” That is, the lists of items (in both Examples 1 and 2) can mean only a, or only b, or only c, or any combination of a, b and c (e.g. ab, ac, be, or abc).

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

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

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• 2014
  • 2014-03-21 EP EP14718498.0A patent/EP3027929A1/de not_active Withdrawn
  • 2014-03-21 WO PCT/US2014/031410 patent/WO2015016983A1/en active Application Filing
  • 2014-07-15 AR ARP140102607A patent/AR096919A1/es active IP Right Grant
  • 2014-07-31 CN CN201420429486.6U patent/CN204253693U/zh not_active Expired - Lifetime

Non-Patent Citations (1)

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