CN110043585B - Wet braking drive axle - Google Patents

Wet braking drive axle Download PDF

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Publication number
CN110043585B
CN110043585B CN201910348916.9A CN201910348916A CN110043585B CN 110043585 B CN110043585 B CN 110043585B CN 201910348916 A CN201910348916 A CN 201910348916A CN 110043585 B CN110043585 B CN 110043585B
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CN
China
Prior art keywords
return spring
flange
brake
shell
friction plate
Prior art date
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Active
Application number
CN201910348916.9A
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Chinese (zh)
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CN110043585A (en
Inventor
金刚强
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang Jindao Technology Co ltd
Original Assignee
Zhejiang Jindao Technology Co ltd
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Priority to CN201910348916.9A priority Critical patent/CN110043585B/en
Publication of CN110043585A publication Critical patent/CN110043585A/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/14—Torque-transmitting axles composite or split, e.g. half- axles; Couplings between axle parts or sections
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/16—Axle housings
    • B60B35/163—Axle housings characterised by specific shape of the housing, e.g. adaptations to give space for other vehicle elements like chassis or exhaust system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
    • 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
    • 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/028—Gearboxes; Mounting gearing therein characterised by means for reducing vibration or noise
    • 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
    • F16D2121/02—Fluid pressure
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Abstract

The invention discloses a wet brake drive axle which comprises an axle housing, an input assembly, a first brake assembly, a first half axle, a first hub component, a second half axle, a second brake assembly and a second hub component, wherein the second brake assembly has the same structure as the brake assembly; the first brake assembly and the second brake assembly can compensate the abrasion of the friction plate so as to prolong the service life of the friction plate, and the input assembly can be provided with a buffer mechanism, so that the influence of the vibration of the drive axle on the transmission can be effectively reduced, and the service life of the drive axle is prolonged.

Description

Wet braking drive axle
Technical Field
The invention relates to the technical field of automobiles, in particular to a wet braking drive axle.
Background
As is well known, the use condition of engineering machinery is relatively bad, at present, the domestic engineering machinery axle product market is still mainly based on a dry brake driving axle, and meanwhile, the dry driving axle adopts an external dry brake, so that the dry driving axle is greatly influenced by environmental factors such as humidity, freezing, dust and the like, the braking performance is unstable, and the service life is short; the wet brake is built-in, is basically not influenced by environmental factors, has long service life and safe and reliable braking, and has wide application in the existing engineering machinery.
In the prior art, a wet brake drive axle is applied to a forklift truck, for example, a chinese patent document with publication number CN107265354a discloses an integrated wet brake drive axle for forklift truck driving and parking, which comprises an input assembly, an axle housing, a first half axle, a second half axle, a spline housing, a fixed gear ring, and a first brake assembly and a second brake assembly positioned in the axle housing.
In addition, the power of the existing wet brake drive axle is often provided by a speed changer, so that the vibration transmitted by a hub on the drive axle is easily transmitted to the speed changer, when the speed changer body is subjected to the vibration, the vibration of an automobile is caused, the noise with different degrees is generated, meanwhile, the vibration of the speed changer body also easily causes the damage of the internal parts of the speed changer, and in the Chinese patent document with the publication number of CN109185420A, a transmission shaft is arranged between an input shaft of the speed changer and the drive axle, so that the direct connection of the speed changer and the drive axle is avoided, but the efficiency of the speed changer is reduced, and the volume and the cost of the wet brake drive axle are also increased.
Disclosure of Invention
A first object of the present invention is to provide a brake assembly, which can automatically adjust the clearance between the piston and the friction plate according to the abrasion condition of the friction plate, so that the braking force of the brake can be maintained at a normal level for a long time.
The second object of the present invention is to provide an input assembly, which is provided with a buffer mechanism, so that the impact of the vibration of the drive axle on the transmission can be effectively reduced, the service life of the drive axle can be prolonged, and compared with the existing buffer mechanism, the buffer mechanism has small volume and high space utilization rate, and is more suitable for forklift installation.
In order to achieve the first object, the present invention adopts the following technical scheme:
the brake assembly comprises an inner friction plate, an outer friction plate, a bearing plate, an annular piston, a return spring seat and a return spring screw, wherein the inner friction plate, the outer friction plate, the bearing plate, the outer friction plate and the first shell are circumferentially positioned and axially movably matched, the inner friction plate and the first half shaft are circumferentially positioned and axially movably matched, a plurality of annular inner friction plates and outer friction plates are alternately overlapped with each other, the annular piston moves between a braking position and a non-braking position, the return spring enables the annular piston to move from the braking position to the non-braking position, a plurality of second mounting holes are uniformly distributed on the side surface of the annular piston, the return spring seat is mounted in the second mounting holes in an interference fit manner, the return spring screw penetrates through the return spring seat and is mounted on the first shell, one end of the return spring is sleeved on the return spring screw, and the other end of the return spring is abutted on the return spring screw.
The travel of the return spring seat is limited by the return spring screw to be a first gap, the annular piston and the return spring seat are in interference fit and move together, and when the inner friction plate and the outer friction plate are in an unworn state, the displacement travel between the braking position and the non-braking position of the annular piston is not larger than the first gap; when the inner friction plate and the outer friction plate are worn, the annular piston and the return spring seat are still in interference fit and fixed after relative displacement is generated, and the return spring screw limits the stroke of the return spring seat to be a first clearance, so that the displacement stroke between the braking position and the non-braking position of the annular piston is the first clearance.
Preferably, the first flange is arranged on the return spring screw, the central hole of the return spring seat is a step hole, one end of the return spring is abutted against the first flange of the return spring screw, and the other end is abutted against the step of the central hole of the return spring seat.
Preferably, the distance between the first flange and the return spring seat is a first clearance, and when the annular piston moves from the non-braking position to the braking position, the first flange can prop against the return spring seat, so that the travel of the return spring seat is limited to be the first clearance.
Preferably, the distance between the first flange and the return spring seat is a first gap, and when the annular piston moves from the non-braking position to the braking position abutting the outer friction plate, the first flange can abut the return spring seat, thereby limiting the travel of the return spring seat to the first gap.
Preferably, one side surface of the annular piston can be propped against the outer friction plate, the other side surface of the annular piston can be propped against the first shell, a first annular groove and a second annular groove are formed in the circumferential side wall of the annular piston, and a first sealing ring and a second sealing ring are respectively arranged in the first annular groove and the second annular groove.
Preferably, the bearing plate is annular, the bearing plate is coaxial with the inner friction plate and the outer friction plate and props against the outer friction plate, and the bearing plate and the annular piston are respectively positioned at different sides of the inner friction plate and the outer friction plate.
Preferably, a mandrel is further arranged, the mandrel is in circumferential positioning fit with the outer friction plate, a plurality of fourth mounting holes are uniformly distributed on the bearing plate in circumference, and the mandrel penetrates through the fourth mounting holes and fixes the bearing plate in the first shell.
Preferably, a first check ring and a second check ring are further arranged, the first check ring and the second check ring are sleeved on the first half shaft and are coaxial with the inner friction plate, and the first check ring and the second check ring are positioned on two sides of the inner friction plate, so that the axial movement range of the inner friction plate is limited.
Due to the adoption of the technical scheme, the invention has the following optimization on the basis of the prior art:
in consideration of the abrasion condition of the friction plate in daily use, a compensation structure is additionally arranged in the brake assembly, namely, the return spring seat and the annular piston are in interference fit, in the braking process, the annular piston drives the return spring seat to move towards the direction of the inner friction plate and the direction of the outer friction plate, when the piston reaches a braking point of the piston abutting against the outer friction plate, the movement distance between the annular piston and the return spring seat is a first gap, the inner friction plate and the outer friction plate are free from abrasion, when the inner friction plate and the outer friction plate are abraded, the annular piston drives the return spring seat to move towards the direction of the friction plate, when the braking point is reached, the movement distance between the return spring seat is the first gap, the movement distance between the annular piston and the friction plate is the abrasion thickness of the first gap, and in the braking process, the return spring seat drives the annular piston to move towards the direction far away from the friction plate, so that the movement distance between the annular piston and the first gap is the first gap, the purpose of compensating the friction plate is achieved, the braking distance is always kept unchanged in the use process, the friction plate is ensured, the abrasion is also durable, and the maintenance cost is reduced.
In order to achieve the second object, the present invention adopts the following technical scheme:
the input assembly comprises a differential mechanism seat, a differential mechanism, a power input shaft, an input flange and a brake flange, wherein the differential mechanism, the power input shaft, the input flange and the brake flange are arranged on the differential mechanism seat, the first bevel gear, the power input shaft, the second bevel gear, the first side gear and the first side gear are integrally formed on the power input shaft, the differential mechanism comprises a differential mechanism shell, a first planet gear, a second side gear and a first side gear, the differential mechanism shell is arranged on the differential mechanism seat and can rotate on the differential mechanism seat, the second bevel gear is fixed on the differential mechanism shell, the second bevel gear is meshed with the first bevel gear, the first planet gear is rotatably arranged in the differential mechanism shell, the first side gear and the second side gear are respectively positioned on the left side and the right side of the differential mechanism shell, the first side gear and the second side gear are both meshed with the first planet gear, and the first side shaft penetrates through the differential mechanism shell and is fixedly spliced with the first side gear, and the second side shaft penetrates the differential mechanism shell and is fixedly spliced with the second side gear; compared with the prior art, the brake flange is matched with the power input shaft through a spline and fixed through a fastener, the input flange is matched with the brake flange through spline transmission, and the input flange can axially float on the brake flange.
Preferably, the brake flange is provided with a first central hole, the inner half section of the first central hole is a spline hole matched with the power input shaft, and the outer half section of the first central hole is a spline hole matched with the outer wall of the input flange.
Preferably, a dust ring is arranged between the input flange and the braking flange, and the dust ring is sleeved on the input flange and positioned at the outer port of the first central hole of the braking flange.
Preferably, the first central hole of the brake flange is a step hole, the inner half section aperture of the first central hole is smaller than the outer half section aperture of the first central hole, a first nut is connected to one end of the power input shaft extending into the first central hole of the brake flange in a threaded manner, and the first nut is abutted to and fixed with the step in the first central hole of the brake flange.
Preferably, the differential mechanism seat is provided with a first mounting hole, the power input shaft and the braking flange are mounted on the first mounting hole, the power input shaft is sleeved with a sealing ring, a spacer bush and two first bearings, the two first bearings are matched with the first mounting hole and the power input shaft, the spacer bush is located between the two first bearings, and the sealing ring is tightly attached to the first nut.
Preferably, a first oil seal is further arranged, the first oil seal is located at the port of the first mounting hole and sleeved on the braking flange, and the first oil seal is in interference fit with the first mounting hole and the braking flange.
Preferably, a parking brake is also provided, which is mounted on the differential carrier by means of a fastening element and which can clamp the brake flange against rotation.
Due to the adoption of the technical scheme, the invention has the following optimization on the basis of the prior art:
the input flange and the brake flange are additionally arranged between the gearbox and the input assembly, compared with the existing transmission shaft additionally provided, only one input flange which is coaxial with the power input shaft and can axially float relative to the brake flange is additionally arranged, so that vibration between the input assembly and the gearbox is only transmitted to the input flange, and the vibration can be counteracted through the axial float of the input flange, so that the independence of the input assembly and the gearbox is improved, the structure is more compact and reasonable, the small-size space utilization rate is high, and the device is more suitable for forklift installation.
The invention also provides a drive axle comprising the brake assembly and the input assembly.
Preferably, the axle further comprises an axle housing, a first half axle, a first hub component, a second half axle, a second brake assembly and a second hub component, wherein the second brake assembly is identical to the brake assembly in structure, the axle housing comprises a second housing, a first housing and a third housing, the middle section of the first housing is cylindrical, two ends of the middle section of the first housing are provided with horn-shaped openings, the first brake assembly and the second brake assembly are identical in structure, the first hub component and the second hub component are identical in structure, the input assembly is mounted on the first housing, the first brake assembly is positioned at the left half section of the first housing, the first hub component is mounted on the second housing, the second housing is fixed at the left end of the first housing, the right half section of the first half axle is connected with the input assembly, the first half axle is connected with the first hub component through the first brake assembly, the second brake assembly is positioned at the right half section of the first housing, the second hub component is mounted on the third housing, the third housing is fixed at the right end of the first housing, the second hub component is connected with the second hub component through the second hub component.
Drawings
FIG. 1 is a schematic illustration of the wet brake drive axle of the present invention;
FIG. 2 is a top view of FIG. 1;
FIG. 3 is a cross-sectional view A-A of FIG. 1;
FIG. 4 is an enlarged view of a portion of the wet brake drive axle of the present invention at O of FIG. 3;
FIG. 5 is an enlarged view of a portion of the wet brake drive axle of the present invention at P of FIG. 3;
FIG. 6 is a schematic illustration of the wet brake drive axle of the present invention in a brake released condition (with no friction plate wear);
FIG. 7 is a schematic illustration of the braking state of the wet brake drive axle of the present invention (friction plates are not worn);
FIG. 8 is a schematic illustration of the wet brake drive axle of the present invention in a brake released condition (friction plate wear);
fig. 9 is a schematic view of the braking state of the wet brake drive axle of the present invention (abrasion of the friction plate).
Reference numerals illustrate: 1. a bridge housing; 11. a first housing; 12. a second housing; 13. a third housing; 2. an input assembly; 3. a first half shaft; 4. a first brake assembly; 5. a first hub assembly; 6. a second half shaft; 7. a second brake assembly; 8. a second hub assembly; 20. a differential housing; 201. a first mounting hole; 21. a differential; 22. a power input shaft; 221. a first bevel gear; 23. an input flange; 24. a brake flange; 25. a dust ring; 26. a first nut; 27. a spacer bush; 28. a first oil seal; 29. a first bearing; 41. an inner friction plate; 42. an outer friction plate; 43. an annular piston; 44. a return spring seat; 45. a return spring screw; 46. a return spring; 47. a first gap; 48. a second gap; 49. a third gap; 432. a second mounting hole; 433. a first ring groove; 434. a second ring groove; 451. a first flange; 71. a mandrel; 72. a pressure bearing plate; 73. a first retainer ring; 74. the second check ring; 75. an oil chamber; 9. a second planetary gear; 211. a differential case; 212. a first planetary gear; 213. a second side gear; 214. a first half-shaft gear; 215. a second bevel gear; 111. a parking brake bracket; 112. a parking brake; 113. a speed sensor; 114. an oil level port; 115. a fuel filler; 116. an oil drain port; 121. a vent port; 122. a first mounting surface.
Detailed Description
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
The wet brake driving axle shown in fig. 1 and 2 comprises an axle housing 1, an input assembly 2, a first hub component 5 and a second hub component 8, wherein the second hub component 8 is identical to the first hub component 5 in structure, the axle housing 1 comprises a first shell 11, a second shell 12 and a third shell 13, the middle section of the first shell 11 is cylindrical, two ends of the first shell 11 are provided with horn-shaped openings, the first shell 11 and the third shell 13 are identical in structure and are fixed at two ends of the first shell 11 through a circle of uniformly distributed hexagon screws, the input assembly 2 is fixed on the first shell 11 through a circle of uniformly distributed hexagon screws, the first hub component 5 is mounted on the second shell 12, and the second hub component is mounted on the third shell 13.
The upper parts of the two ends of the first shell 11 are provided with air discharge ports 121, the air discharge ports 121 are positioned in the conical area of the bell mouth, the air discharge ports 121 are only required to be opened to discharge air in the oil cavity 75 when pressure oil is initially added into the wet brake drive axle, and the air discharge ports 121 are required to be blocked by air discharge screws at other times, so that the sealing effect is achieved.
A parking brake bracket 111 is also fixed at the front end of the first housing 11 by a screw, a parking brake 112 is mounted on the parking brake bracket 111, and the parking brake 112 can control the parking brake bracket to clamp the brake flange 24 so that the brake flange 24 cannot rotate.
A speed sensor 113 is installed at a middle position of the upper portion of the first housing 11 for monitoring a real-time rotation speed of the second bevel gear 215 of the input assembly 2; in this embodiment, the second bevel gear 215 is preferably a spiral bevel gear.
An oil level port 114 is provided at the rear end of the first housing 11, and the center of the oil level port 114 is located on the same horizontal plane as in fig. 3, so as to facilitate observation of the specific condition of the lubricating oil in the first housing 11.
A fuel filler 115 is provided on the upper right side of the first housing 11, and is normally sealed by a screw plug and an O-ring.
An oil drain 116 is provided at the lower left side of the first housing 11, and is normally sealed by a magnetic oil drain bolt and an O-ring.
The driving axle shown in fig. 3 comprises an axle housing 1, an input assembly 2, a first half shaft 3, a first brake assembly 4, a first hub component 5, a second half shaft 6, a second brake assembly 7 and a second hub component 8, wherein the axle housing 1 comprises a second housing 12, a first housing 11 and a third housing 13, the middle section of the first housing 11 is cylindrical, two ends of the middle section are provided with horn-shaped openings, the first brake assembly 4 and the second brake assembly 7 are identical in structure, the first hub component 5 and the second hub component 8 are identical in structure, the input assembly 2 is mounted on the first housing 11, the first brake assembly 4 is positioned on the left half section of the first housing 11, the first hub component 5 is mounted on the second housing 12, the second housing 12 is fixed on the left end of the first housing 11 through a circle of uniformly distributed hexagonal screws, the right half shaft 3 is connected with the input assembly 2, the first half shaft 3 is connected with the first hub component 5 through the first brake assembly 4, the second half shaft 7 is positioned on the right half shaft 7 is connected with the second half shaft assembly 8 through the second half shaft 11, and the second half shaft assembly 7 is connected with the third hub component 7 on the right half shaft 11 through the second housing 12, and the second half shaft component is uniformly distributed on the right half shaft 7 is mounted on the second housing 12 through the second half shaft 7.
The input assembly 2 shown in fig. 4 comprises a differential gear seat 20, a differential gear 21, a power input shaft 22, a first bevel gear 221, an input flange 23 and a brake flange 24 which are arranged on the differential gear seat 20, wherein the differential gear seat 20 is fixed on the first shell 11 through a circle of uniformly distributed hexagon screws, the power input shaft 22 and the first bevel gear 221 are integrally formed, the first bevel gear 221 is preferably a spiral bevel pinion, the differential gear 21 comprises a differential gear shell 211, a first planetary gear 212, a second half-shaft gear 213 and a first half-shaft gear 214, the differential gear shell 211 is arranged on the differential gear seat 20 and can rotate on the differential gear seat 20, a tapered roller bearing and a second nut are arranged between the differential gear shell 211 and the differential gear seat 20, the tapered roller bearing is sleeved on the differential gear shell 211 and is in interference fit with the differential gear seat 20 and the differential gear shell 211, for ensuring smooth rotation of the differential case 211, a second nut is installed between the tapered roller bearing and the differential housing 20, a second bevel gear 215 is fixed to the differential case 211, the second bevel gear 215 is preferably a spiral bevel gear, the second bevel gear 215 is meshed with a first bevel gear 221, the first planetary gear 212 is rotationally fixed inside the differential case 211, a first half shaft gear 214 and a second half shaft gear 213 are respectively positioned at left and right sides inside the differential case 211, and both the first half shaft gear 214 and the second half shaft gear 213 are meshed with the first planetary gear 212, the first half shaft 3 and the second half shaft 6 penetrate the differential case 211 and are respectively inserted and fixed on the first half shaft gear 214 and the second half shaft gear 213, a first center hole is provided on the brake flange 24, an inner half section of the first center hole is in driving fit with the power input shaft 22 through a spline, and still be equipped with dust ring 25, dust ring 25 is located first centre bore port and overlaps and establish on input flange 23, first centre bore outer half passes through spline and the outer wall transmission cooperation of input flange 23, input flange 23 can be at the axial float on first centre bore, compare with current transmission shaft that adds again like this, only increased an input flange 23 coaxial with power input shaft 22 and can be for braking flange 24 axial float, the vibration between input assembly 2 and the derailleur only transmits to input flange 23, can offset the vibration through the axial float of input flange 23 for the independence of input assembly 2 and derailleur increases, and compact structure is reasonable, small space utilization is high, more be fit for fork truck and install.
In another embodiment of the scheme, a second center hole is formed in the input flange, the second center hole is in transmission fit with the outer wall of the brake flange through a spline, the input flange can axially float on the outer wall of the brake flange, and the dust ring is located at a port of the second center hole and sleeved on the brake flange; in this embodiment, the first central hole may be either a through hole or a blind hole, and in this embodiment it is preferable that the first central hole is a through hole.
Specifically, the first central hole of the brake flange 24 is a stepped hole, the inner half-section aperture of the first central hole is smaller than the outer half-section aperture thereof, a first nut 26 is screwed on one end of the power input shaft 22 extending into the first central hole of the brake flange 24, and the first nut 26 is fixed against the step in the first central hole of the brake flange 24.
Specifically, a dust ring 25 is arranged between the input flange 23 and the brake flange 24, and the dust ring 25 is sleeved on the input flange 23 and is positioned at the outer port of the first central hole of the brake flange 24.
Specifically, the differential mechanism seat 20 is provided with a first mounting hole 201, the power input shaft 22 and the brake flange 24 are mounted on the first mounting hole 201, the power input shaft 22 is sleeved with a sealing ring, a spacer 27 and two first bearings 29, the first bearings 29 are preferably tapered roller bearings, the sealing ring is preferably an O-shaped sealing ring, the two first bearings 29 are in interference fit with the first mounting hole 201 and the power input shaft 22, the spacer 27 is located between the two first bearings 29, the sealing ring is tightly attached to the first nut 26, and an adjusting gasket is further arranged between the spacer 27 and the first bearings 29 located at the outer end.
By the above arrangement, the power input shaft 22 and the brake flange 24 can be smoothly rotated on the differential carrier 20.
Specifically, a first oil seal 28 is further provided, the first oil seal 28 is preferably a framework oil seal, the first oil seal 28 is located at an outer side port of the first mounting hole 201 and is sleeved on the brake flange 24, and the first oil seal 28 is in interference fit with the first mounting hole 201 and the brake flange 24, so that the tightness of the first mounting hole 201 is ensured.
In the present invention in the above structure, power is transmitted from the transmission output shaft flange to the input flange 23 of the transaxle, the input flange 23 is in driving engagement with the brake flange 24 by the spline to transmit power to the brake flange 24, the brake flange 24 and the power input shaft 22 are in driving engagement by the spline to transmit power to the power input shaft 22 and the first bevel gear 221, the first bevel gear 221 and the second bevel gear 215 are in meshing engagement to transmit power to the second bevel gear 215 and the differential case, and then the power is transmitted to the second side gear 213 and the first side gear 214 by the first planetary gear 212 on the differential, the power is transmitted to the first half shaft 3 by the first side gear 214, and the power is transmitted to the second half shaft 6 by the second side gear 213.
The first brake assembly 4 shown in fig. 5 comprises an inner friction plate 41, a bearing plate (72), an outer friction plate 42, an annular piston 43, a return spring 46 and a return spring screw 45 which are positioned in the left half section of the first shell 11, wherein the bearing plate 72 and the outer friction plate 42 are in movable axial fit with the circumferential positioning shaft of the first shell 11, the inner friction plate 41 and the first half shaft 3 are in movable axial fit with each other in the circumferential positioning shaft, the plurality of annular inner friction plates 41 and the outer friction plate 42 are alternately overlapped with each other, the annular piston 43 moves between a braking position and a non-braking position, the return spring 46 moves the annular piston 43 from the braking position to the non-braking position, a return spring seat 44 is further arranged, a plurality of second mounting holes are uniformly distributed on the side surface of the annular piston 43, the return spring seat 44 is in the second mounting holes in an interference fit, the return spring screw 45 passes through the return spring seat 44 and is mounted on the first shell 11, the return spring 46 is sleeved on the return spring screw 45, one end of the return spring seat 44 abuts against the return spring seat 44, and the other end of the return spring 46 abuts against the return spring screw 45.
The outer surface of the return spring seat 44 is a cylindrical surface and is in interference fit with the second mounting hole 432, which is worth noting that the outer surface of the return spring seat 44 may be in other shapes, such as a triangular prism, a cuboid, etc., the corresponding second mounting hole 432 is in interference fit with the outer surface of the return spring seat 44, and the specific form is that the return spring seat 44 and the annular piston 43 can mutually drive each other to move, and when the inner friction plate 41 and the outer friction plate 42 are worn, the travel of the return spring seat 44 is limited by the return spring screw 45 to be the first gap 47, the annular piston 43 and the outer friction plate 42 still have a gap, and the annular piston 43 can still axially move under the action of oil pressure until the end surface abuts against the outer friction plate 42.
Specifically, one side surface of the annular piston 43 can abut against the outer friction plate 42, the other side surface of the annular piston 43 can abut against the first housing 11, a first annular groove 433 and a second annular groove 434 are provided on the circumferential side wall of the annular piston 43, and a first sealing ring and a second sealing ring are respectively provided in the first annular groove 433 and the second annular groove 434.
Specifically, the return spring screw 45 is provided with a first flange 451, one end of the return spring 46 abuts against the first flange 451, the other end abuts against the return spring seat 44, the distance between the first flange 451 and the return spring seat 44 is the first gap 47, when the annular piston 43 moves from the non-braking position to the braking position abutting against the outer friction plate 42, the first flange 451 may abut against the return spring seat 44, so as to limit the travel of the return spring seat 44 to the first gap 47, in this embodiment, the first flange 451 may be disc-shaped or other shape, only when the annular piston 43 moves from the non-braking position to the braking position abutting against the outer friction plate 42, the first flange 451 may abut against the return spring seat 44, in this embodiment, the first flange 451 preferably abuts against the disc-shaped spring seat, and the disc diameter is larger than the inner diameter of the spring seat, so that the return spring seat 44 can be returned.
Specifically, the bearing plate 72 is in a ring shape, the bearing plate 72 is coaxial with the inner friction plate 41 and the outer friction plate 42 and abuts against the outer friction plate 42, the bearing plate 72 and the annular piston 43 are respectively located on different sides of the inner friction plate 41 and the outer friction plate 42, the bearing plate 72 is sleeved on the first half shaft 3, the bearing plate 72 and the annular piston 43 are respectively located on different sides of the inner friction plate 41 and the outer friction plate 42, the mandrel 71 is in circumferential positioning fit with the outer friction plate 42, a plurality of fourth mounting holes are uniformly distributed on the circumference of the bearing plate 72, and the mandrel 71 penetrates through the fourth mounting holes and fixes the bearing plate 72 in the second shell 12.
Specifically, a first retaining ring 73 and a second retaining ring 74 are further provided, the first retaining ring 73 and the second retaining ring 74 are sleeved on the first half shaft 3, and the first retaining ring 73 and the second retaining ring 74 are sleeved coaxially with the inner friction plate 41 and are positioned on two sides of the inner friction plate 41 and the outer friction plate 42, so that a limiting effect is provided for the friction plates, and the axial movement range of the inner friction plate 41 and the outer friction plate 42 is prevented.
Specifically, there are also second planetary gears 9, three second planetary gears 9 are respectively circumferentially and uniformly around the first half shaft 3 and located between the bearing plate 72 and the first hub assembly 5, and two end gears of the second planetary gears 9 are respectively in transmission fit with the first half shaft 3 and the first hub assembly 5.
The second brake assembly 7 is identical in construction to the first brake assembly 4 and includes the above construction.
In the structure, in the state of releasing the brake, the first half shaft 3 transmits power to the second planetary gear 9 through the transmission matched with the second planetary gear 9, and the second planetary gear 9 transmits power to the first hub assembly 5 through the transmission matched with the first hub assembly 5, so that the external appearance is that the left wheel rotates, and the power transmission condition of the right half part and the left half part of the drive axle are the same;
in the braking state in which the annular piston 43 is against the outer friction plate 42, the inner friction plate 41 and the outer friction plate 42 can no longer rotate freely under the action of friction force, and the resistance is transmitted to the first half shaft 3, the second planetary gear 9 and the first hub assembly 5, so that the rotation speed of the left wheel is reduced or stopped, and the resistance transmission condition for the right half part and the left half part of the drive axle are the same.
As shown in fig. 6, in the wet brake release state of the present invention, in which the end face of the smaller diameter side of the annular piston 43 abuts against one of the mounting surfaces in the first housing 11, the name of the mounting surface in the second housing 12 is called a first mounting surface 122 for the convenience of confirmation in this embodiment, the return spring seat 44 is interference fitted with the second mounting hole 432 in the annular piston 43, and the end face of the return spring seat 44 abuts against the first mounting surface 122, the distance between the first flange 451 on the return spring screw 45 and the return spring seat 44 is the first gap 47.
The oil enters the oil cavity 75, the annular piston 43 drives the return spring seat 44 to move from the non-braking position separated from the outer friction plate 42 to the braking position abutting against the outer friction plate 42 until the annular piston 43 reaches the braking point abutting against the outer friction plate 42, namely, as shown in fig. 7, the friction plate of the wet brake drive axle of the present invention is in a non-worn braking state, in which the end face of the annular piston 43 on the larger diameter side abuts against the outer friction plate 42, the end face of the smaller diameter side is still flush with the end face of one end of the return spring seat 44, and the end face of the other end of the return spring seat 44 abuts against the first flange 451 on the return spring screw 45, in which the distance between the return spring seat 44 and the first mounting surface 122 is the first gap 47, and the distance between the end face of the smaller diameter side of the annular piston 43 and the first mounting surface 122 is also the first gap 47, namely, the displacements of the return spring seat 44 and the annular piston 43 are both the first gap 47.
When the inner friction plate 41 and the outer friction plate 42 are worn, the travel of the return spring seat 44 is limited by the return spring screw 45 to be a first gap 47, and the annular piston 43 can still move axially until the end face abuts against the outer friction plate 42, namely, when the inner friction plate 41 and the outer friction plate 42 of the wet brake drive axle are worn, as shown in fig. 9, when the annular piston 43 reaches a braking position abutting against the outer friction plate 42, the end face of the smaller diameter side of the annular piston 43 is no longer flush with the end face of the return spring seat 44, the end face of the return spring seat 44 protrudes a part relative to the end face of the smaller diameter side of the annular piston 43, and the other end face of the return spring seat 44 abuts against the first flange 451 on the return spring screw 45, in this state, the distance between the return spring seat 44 and the first mounting face 122 is the first gap 47, the distance between the end face of the smaller diameter side of the annular piston 43 and the first mounting face 122 is the second gap 48, and the second gap 48 is larger than the first gap 47.
The oil chamber 75 discharges the pressurized oil, the return spring seat 44 moves away from the inner friction plate 41 and the outer friction plate 42 by the return spring 46, and drives the annular piston 43 to move together until reaching the non-braking state as shown in fig. 8, in which the displacement of the return spring seat 44 and the annular piston 43 is the first gap 47, so that there is a third gap 49 between the end face of the smaller diameter side of the annular piston 43 and the first mounting face 122, the sum of the third gap 49 and the first gap 47 is the second gap 48, the end face of the return spring seat 44 protrudes a part of the end face of the return spring seat 44 relative to the end face of the smaller diameter side of the annular piston 43, and the end face of the return spring seat 44 abuts against the first mounting face 122, in which state the distance between the first flange 451 on the return spring screw 45 and the return spring seat 44 is the first gap 47.
It should be noted that, during the process that the annular piston 43 reaches the non-braking position separated from the outer friction plate 42 from the braking point abutting against the outer friction plate 42, no matter whether the inner friction plate 41 and the outer friction plate 42 have abrasion or not, the return spring seat 44 drives the annular piston 43 to move together in the direction away from the inner friction plate 41 and the outer friction plate 42, the moving distance is always the first gap 47 under the limit of the first flange 451 and the first mounting surface 122, that is, the return distance of the annular piston 43 is always the first gap 47, that is, when the annular piston 43 reaches the braking position of the annular piston 43 abutting against the outer friction plate 42 from the non-braking position separated from the outer friction plate 42 next time, the required displacement of the annular piston 43 is always the first gap 47, so that the purpose of compensating the abrasion of the inner friction plate 41 and the outer friction plate 42 is achieved, the braking distance is always kept unchanged during the use of the brake assembly, the braking effect is ensured, the inner friction plate 41 and the outer friction plate 42 are also more durable, and the maintenance cost of the inner friction plate 41 and the outer friction plate 42 is reduced.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives, and variations may be made in the above embodiments by those skilled in the art without departing from the spirit and principles of the invention. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. The wet brake drive axle comprises an axle housing (1), an input assembly (2), a first brake assembly (4), a first half shaft (3), a first hub component (5), a second half shaft (6), a second brake assembly (7) and a second hub component (8), wherein the second brake assembly (7) has the same structure as the first brake assembly (4), the axle housing (1) comprises a first shell (11), a second shell (12) and a third shell (13), the first brake assembly (4) has the same structure as the second brake assembly (7), the first hub component (5) has the same structure as the second hub component (8), the input assembly (2) is arranged on the first shell (11), the first brake assembly (4) is positioned at the left half section of the first shell (11), the first hub component (5) is arranged on the second shell (12), the second shell (12) is fixed at the left end of the first shell (11), the right half shaft assembly (3) is connected with the first half shaft assembly (3) through the first hub component (3) and the second hub component (8) is arranged on the first half shaft (7) in a connecting mode, the third shell (13) is fixed at the right end of the first shell (11), the left section of the second half shaft (6) is connected with the input assembly (2), and the second half shaft (6) is connected with the second hub assembly (8) through the second brake assembly (7);
the input assembly (2) comprises a differential mechanism seat (20), a differential mechanism (21) arranged on the differential mechanism seat (20), a power input shaft (22) and an input flange (23), wherein a first bevel gear (221) is integrally formed on the power input shaft (22), the differential mechanism (21) comprises a differential mechanism shell (211), a first planetary gear (212), a second side gear (213) and a first half-shaft gear (214), the differential mechanism shell (211) is arranged on the differential mechanism seat (20) and can rotate on the differential mechanism seat (20), the differential mechanism shell (211) is fixedly provided with the second bevel gear (215), the second bevel gear (215) is meshed with the first bevel gear (221), the first planetary gear (212) is rotatably arranged inside the differential mechanism shell (211), the first half-shaft gear (214) and the second half-shaft gear (215) are respectively positioned on the left side and the right side of the inside of the differential mechanism shell (211), the first half-shaft gear (214) and the second half-shaft gear (215) are respectively meshed with the first planetary gear (212), the power input shaft (23) is fixedly connected with the differential mechanism (22) in a penetrating manner, the first half-shaft (23) is meshed with the differential mechanism shell (3), the second half shaft (6) penetrates through the differential shell (211) and is fixedly spliced with the second half shaft gear (215);
it is characterized in that the method comprises the steps of,
the first brake assembly (4) comprises an inner friction plate (41), a pressure bearing plate (72), an outer friction plate (42), an annular piston (43), a return spring (46), a return spring seat (44) and a return spring screw (45) which are arranged in the first shell (12), the pressure bearing plate (72), the outer friction plate (42) and the first shell (12) are in circumferential positioning axial clearance fit, the inner friction plate (41) and the first half shaft (3) are in circumferential positioning axial clearance fit, a plurality of annular inner friction plates (41) and the outer friction plate (42) are alternately overlapped with each other, the annular piston (43) moves between a braking position and a non-braking position, the return spring (46) enables the annular piston (43) to move from the braking position to the non-braking position, a plurality of second mounting holes are uniformly distributed on the side face of the annular piston (43), the return spring seat (44) is in interference fit in the second mounting holes, the return spring screw (45) penetrates the return spring seat (44) and is mounted on the first shell (11), the return spring (46) is sleeved on the return spring (45), and the other end of the return spring (46) abuts against the return spring seat (45).
2. A wet brake drive axle according to claim 1, characterized in that a brake flange (24) is further provided, the input flange (23) being in driving engagement with the brake flange (24), the brake flange (24) being in driving engagement with the power input shaft (22).
3. A wet brake drive axle according to claim 2, characterized in that the brake flange (24) is splined to the power input shaft (22) and secured by fasteners, the input flange (23) is splined to the brake flange (24), and the input flange (23) is axially movable over the brake flange (24).
4. A wet brake drive axle according to claim 3, characterized in that the brake flange (24) is provided with a first central bore, the inner half of which is a splined bore for engagement with the power input shaft (22), and the outer half of which is a splined bore for engagement with the outer wall of the input flange (23).
5. A wet brake drive axle according to claim 4, characterized in that a dust ring (25) is arranged between the input flange (23) and the brake flange (24), said dust ring (25) being arranged over the input flange (23) and being located at the outer end of the first centre hole of the brake flange (24).
6. The wet brake drive axle according to claim 4, wherein the first central hole of the brake flange (24) is a stepped hole, the inner half-section aperture of the first central hole is smaller than the outer half-section aperture of the first central hole, a first nut (26) is connected to one end of the power input shaft (22) extending into the first central hole of the brake flange (24) in a threaded manner, and the first nut (26) is fixed against the step in the first central hole of the brake flange (24).
7. A wet brake drive axle according to claim 1, characterized in that the return spring screw (45) limits the travel of the return spring seat (44) to a first clearance (47), the annular piston (43) and the return spring seat (44) being co-movable in an interference fit, the displacement travel between the braked position and the unbraked position of the annular piston (43) being no greater than the first clearance (47) when the inner friction plates (41) and the outer friction plates (42) are in an unworn state; when the inner friction plate (41) and the outer friction plate (42) are worn, the annular piston (43) and the return spring seat (44) are in interference fit and fixed after relative displacement, the return spring screw (45) limits the stroke of the return spring seat (44) to be a first gap (47), and therefore the displacement stroke between the braking position and the non-braking position of the annular piston (43) is the first gap (47).
8. A wet brake drive axle according to claim 7, wherein the return spring screw (45) is provided with a first flange (451), the central hole of the return spring seat (44) is a stepped hole, one end of the return spring (46) abuts against the first flange (451) of the return spring screw (45), and the other end abuts against the central hole step of the return spring seat (44).
9. A wet brake drive axle according to claim 8, wherein the distance between the first flange (451) and the return spring seat (44) is a first gap (47), and the first flange (451) is adapted to abut the return spring seat (44) when the annular piston (43) is moved from the non-braking position to the braking position, thereby limiting the travel of the return spring seat (44) to the first gap (47).
10. A wet brake drive axle according to claim 1, further comprising a first collar (73) and a second collar (74), the first collar (73) and the second collar (74) being fitted over the first half-shaft (3) and being coaxial with the inner friction plate (41), the first collar (73) and the second collar (74) being located on opposite sides of the inner friction plate (41) so as to limit the axial play range of the inner friction plate (41).
CN201910348916.9A 2019-04-28 2019-04-28 Wet braking drive axle Active CN110043585B (en)

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Publication number Priority date Publication date Assignee Title
CN111878528A (en) * 2020-07-10 2020-11-03 浙江金道科技股份有限公司 Drive axle and service brake assembly thereof
CN111775629B (en) * 2020-07-10 2024-01-30 浙江金道科技股份有限公司 Driving axle
CN112223956A (en) * 2020-10-15 2021-01-15 浙江金道科技股份有限公司 Wet-type axle and box integrated drive axle for forklift

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DE102005051500B3 (en) * 2005-10-26 2007-07-05 Gkn Driveline International Gmbh Determining torque acting on multi-plate friction clutch in vehicle, includes force measurement system within clutch casing, acted upon by plate carrier stud when clutch is operated
CN102494055A (en) * 2011-12-06 2012-06-13 天津工程机械研究院 Multi-disk wet-type brake for loading machine
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