WO2016015864A1 - Mécanisme d'entraînement - Google Patents

Mécanisme d'entraînement Download PDF

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Publication number
WO2016015864A1
WO2016015864A1 PCT/EP2015/001563 EP2015001563W WO2016015864A1 WO 2016015864 A1 WO2016015864 A1 WO 2016015864A1 EP 2015001563 W EP2015001563 W EP 2015001563W WO 2016015864 A1 WO2016015864 A1 WO 2016015864A1
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WO
WIPO (PCT)
Prior art keywords
drive
stage
flange
gear
drum
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2015/001563
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English (en)
Inventor
Luigino Pozzo
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PMP PRO-MEC SpA
Original Assignee
PMP PRO-MEC SpA
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Filing date
Publication date
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Publication of WO2016015864A1 publication Critical patent/WO2016015864A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28C—PREPARING CLAY; PRODUCING MIXTURES CONTAINING CLAY OR CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28C5/00—Apparatus or methods for producing mixtures of cement with other substances, e.g. slurries, mortars, porous or fibrous compositions
    • B28C5/42—Apparatus specially adapted for being mounted on vehicles with provision for mixing during transport
    • B28C5/4203—Details; Accessories
    • B28C5/4206—Control apparatus; Drive systems, e.g. coupled to the vehicle drive-system
    • B28C5/421—Drives
    • B28C5/4217—Drives in combination with drum mountings; Drives directly coupled to the axis of rotating drums
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
    • F16D3/185—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth radial teeth connecting concentric inner and outer coupling parts
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/207—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially inwardly from the coupling part
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing

Definitions

  • the present invention relates to a drive according to the characteristics of the pre-characterizing part of claim 1._,
  • the present invention also relates to a concrete mixer vehicle provided with a concrete mixing rotating drum which is provided with a drive, according to the characteristics of the pre-characterizing part of claim 28.
  • the drum must be operated with a maximum rotational speed of 14-20 rpm and a maximum torque ranging from 30000 Nm up to 60000 Nm and beyond, depending on the capacity of the mixing drum itself.
  • the drum can be 3 to 4 m long, for example and without limitation to the application of the present invention, and it is secured at its ends on a frame with tractor for the road transportation of concrete.
  • a key feature to be observed is that the rotation speed of the drum must be independent from the operating speed of the engine of the tractor vehicle. Due to the fact that on the tractor a power take-off is not available which is able to supply the speed and torque which are required for the operation of the .
  • the usually adopted solution consists in interposing a system consisting of a hydraulic pump and a hydraulic motor between the engine of the tractor vehicle and the drum.
  • the axial piston hydraulic motor is the most commonly used because it represents the best compromise between power output, size and costs.
  • a hydraulic motor of this type is able to provide maximum power at speeds that are between 1800 and 2500 rpm. Due to the rotation speed of the drum and the rotation speed of the hydraulic motor it is necessary to interpose a mechanical reducer between them which ensures a minimum reduction ratio of about 1 :100. For this kind of use a planetary gear reducer with multiple reduction stages is typically used, due to size and reliability reasons.
  • the gear unit constituting the drive system is usually coaxially installed with respect to the drum and at an external position with respect to the inner compartment of the drum, while solutions are present in which the hydraulic motor is placed in an aligned condition with respect to the drive system as well as solutions in which the hydraulic motor is arranged in an axially offset position with respect to the drive system.
  • the installation occurs in correspondence of the opposite side of the drum with respect to the introduction and extraction mouth of the concrete.
  • Patent SU 1364486 describes a drive for a mixing drum of a concrete mixer vehicle in which part of the gears is fixed internally to the body of the drum, wherein the first and the second stage of the gear unit are positioned in an outer shell, and the third stage is located within an shell which is located internally to the drum, the outer shell having a wall thickness greater than the thickness of the wall of the inner shell.
  • Patent US4006946 describes a roller bearing for the shaft of a cement-mixer drum, universally jointed on a shaft of a planetary-gear train driving the drum shaft through a gear coupling with arcuate teeth, in which the roller bearing is provided with an inner ring which is fixed to the shaft of the drum and with an outer ring which is fixed on a surrounding drive housing, such outer ring being axially split into two halves each accommodating a set of barrel-shaped rollers which are held in respective cages, peripherally offset from each other.
  • Patent DE8326270 discloses a planetary gear with power take-off which acts on a first stage consists of a central inner gear, planetary-gears and planetary-gear supports, in which the rotation movement of the planetary-gear support occurs through a curved teeth coupling using a spherical bearing for the output coupling, and further in which the shaft of the output joint protrudes towards the inside of the gear being supported on a spherical bearing with a convex radius of curvature and the planetary- gear support being axially supported through roller bearings.
  • Patent DE2948936 describes a planetary gear in which the rotation axis lies on the pins of the planetary-gear support of the last stage of the drive, and wherein in correspondence of such coupling a ring is present which has with an outer arcuated profile rotatably associated with a counter-shaped supporting profile.
  • Patent US4124304 describes a device for driving a drum of a concrete mixer vehicle comprising a casing fixedly mounted on the vehicle frame and a driving shaft connected to the drum by a universal coupling consisting of a driving member concentrically connected to the driving shaft and rotatably supported by the casing through a self-aligning roller bearing, and a driven member which is fixed to the driven drum which engages with the driving member with a spherical bearing disposed there between, the self-aligning roller bearing and spherical bushing being concentrically arranged to rotate about a common center of rotation, and the connecting means being arranged on a reference plane in which the center of rotation lies.
  • Patent US3788610 describes a lubricant system for the support unit of a concrete mixer vehicle comprising a lubricant chamber enclosing the drive connection between the drive shaft and drum.
  • Patent WO 2013/045070 describes a drive device for a drum of a concrete mixer vehicle which includes a multistage epicyclic gear-reduction device which comprises at least two reduction stages of which at least a first stage is housed within the volume of the drum of the concrete mixer vehicle while at least another stage is housed externally with respect to the volume of the drum of the concrete mixer vehicle.
  • Prior art solutions have many problems.
  • One problem is relative to the overall size of the concrete mixer vehicle and to its weight.
  • the size of the drive while apparently looking negligible if compared to the overall size of the concrete mixer vehicle, are very important because it is necessary to provide enough space on the frame of the concrete mixer vehicle to house the drive and the corresponding hydraulic motor, in an intermediate position between the concrete containing drum and the operating cab.
  • Prior art solutions involve a considerable space required for the installation of such devices, with the consequence that it is necessary to use greater drum supporting frames with further increasing of costs and increasing of weights and consumption.
  • the drum is mounted on roller supports which allow its rotation and which support the weight of the drum and the concrete contained in it. Part of the weight is also released on the drive system.
  • a further drawback is due to the fact that, during the movement of the mixer on the road, the drum, the frame and the drive system are subject to high stresses with the consequence that torsion phenomena occurs involving the frame of the concrete mixer vehicle itself. As a consequence reciprocal movements are present between the rotating drum and the support frame on which also the drive system and hydraulic motor are fixed.
  • prior art solutions provide for the use of an assembly which is known as bell coupling joint, which allows the drive of the rotational motion and at the same time allows the reciprocal displacement between the drum and part of the drive system which is fixed to the frame.
  • Such elastic means may be subject to premature aging resulting in the loss of their functionality, due to the fact that they are exposed to temperature change, sun, weather conditions, etc.
  • the need to provide sizes of the pads suitable for the application and sizes of the mechanical components able to withstand the induced vibrations at least in part compromises the economic benefits obtained by the adoption of such systems, so as to cause this solution to be more expensive than conventional systems, in addition to the fact that no reduction of the weights and of the overall dimensions is not provided for the group comprising the drive and the hydraulic motor.
  • the aim of the present invention is to provide a drive for the drum of a concrete mixer vehicle which allows a reduction of the overall size of the drive itself and in particular of the portion of the drive which is inserted within the volume of the drum of the concrete mixer vehicle at the same time not increasing the size of the drive on the external side of the drum itself.
  • the aim of the present invention is to solve the above mentioned problems and disadvantages of the prior art systems, providing a drive for a drum of a concrete mixer vehicle which is compact and reliable allowing a reduction of the overall sizes.
  • a further aim of the present invention is to allow an effective releasing of the portion of the weight of the drum of the concrete mixer vehicle which weights down over the drive while ensuring a reduction of the drive itself while maintaining its reliability.
  • Fig. 1 schematically shows a concrete mixer vehicle comprising the drive according to the present invention.
  • Fig. 2 schematically shows a drum for a concrete mixer vehicle comprising the drive according to the present invention.
  • Fig. 3 shows the detail which is indicated with "A” in Fig 2.
  • Fig. 4 is a schematic exploded view of the drive according to the present invention.
  • Fig. 5, Fig. 6, Fig. 7, Fig. 8 are views showing a mounting sequence of one of the components of the drive according to the present invention.
  • Fig 9 schematically shows a sectional view of a prior art drive.
  • Fig 10 schematically shows a sectional view of the drive according to the present invention.
  • Fig. 11 , Fig. 12, Fig. 13, Fig. 14, Fig. 15 schematically show the reciprocal movement which is allowed between the components of the drive according to the present invention.
  • Fig 16 shows the detail which is indicated with "B” in Fig 14.
  • Fig 17 shows the detail which is indicated with "C” in Fig 15.
  • Fig 18 shows the detail which is indicated with “D” in Fig 15.
  • Fig 19 shows a detail of the coupling system according to the invention.
  • Fig 20 shows one of the elements of the coupling system according to the invention.
  • Fig. 21 , Fig. 22 show the mounting condition of the element of Fig. 20 inside the drive.
  • Fig. 23, Fig. 24 show the operation of the coupling system according to the invention. Description of the invention
  • the concrete mixer vehicle (8) consists of a tractor vehicle (6) which is operated by a respective motor (4) of the tractor vehicle and a frame (7) on which the rotating drum (3) is mounted resting on supports (5).
  • the rotation of the drum (3) occurs (Fig. 2, Fig 3) by means of a drive system (1 ) driven by a respective hydraulic motor (2), which puts in rotation the drum (3) of the concrete mixer vehicle (8) within which the continuous mixing occurs of the concrete which is contained in the drum (3) itself.
  • the rotation occurs in two directions, one direction being intended for mixing and one direction and being intended for discharging the concrete which is contained into the drum.
  • the motor which puts in rotation the drum (3) is a hydraulic motor, even more preferably an axial piston hydraulic motor.
  • the solution according to the present invention provides the interposition of a drive system (1) consisting of a planetary gear unit with multiple reduction stages.
  • the gear unit constituting the drive system (1) is preferably installed according to a coaxial arrangement with respect to the drum (3) in correspondence of the opposite side of the drum (3) with respect to the introduction and extraction mouth of the concrete.
  • the drive (1) is constructed (Fig. 3, Fig 4, Fig 10) according to a configuration with planetary-gears and planetary-gears supports.
  • the configuration includes 3 stages of planetary-gears and planetary- gears supports
  • the present invention should be intended as being also applicable in the case of solutions in which a lower or higher number of stages is present, as for example drive configuration with two stages of planetary-gears and planetary-gears supports, drive configuration with four stages of planetary-gears and planetary-gears supports, etc.
  • the configuration provides that the last stage of the drive, the third stage in the illustrated embodiment, is a stage which is configured with planetary-gears support (1 ) of the third stage of the fixed type and with a rotating ring-gear (21). In this way, it is the ring-gear (21) itself which transmits the motion to the fixing flange (23) of the drum (3).
  • the guiding element (36') guides the reciprocal misalignment movement between the flange (23) and an element (21) transmitting the rotational motion to the fixing flange (23) of the drum (3), the guiding element (36') sliding in the groove
  • the maximum allowed misalignment (Fig. 12, Fig. 13, Fig. 17, Fig. 1 8) is of at least +1-2 degrees, preferably of at least +/-4 degrees. This allows to take into account the bending of the frame (7) of the concrete mixer vehicle (8) which occur during transportation on the road, preventing the stresses transmitted to the drive (1 ) may lead to a blocking of the same or to its premature wearing, as well as preventing anomalous stresses on the supports of the rotating drum (3) to occur.
  • the solution according to the present invention provides that at least the last stage of the epicyclic drive system, that is the power stage of the same, is housed (Fig. 3) within a chamber (26) obtained at the head of the drum (3), namely in correspondence of the side of the drum (3) which is the opposite side with respect to the side on which there is the intake for the introduction and the taking-out of the concrete. Positioning the epicyclic power stage inside the drum (3) it is allowed to free up space to place two more epicyclic stages at the head of the drive (1 ). In this way a drive (1 ) or reduction gear can be obtained with an extremely high reduction ratio, which makes it possible to use an input hydraulic motor (2) having a reduced size if compared to current standards.
  • the power stage is realized according to a configuration with fixed planetary-gears support and rotating ring-gear (21), so that it is the rotating ring- gear (21) itself which transmits the motion to the fixing flange (23) of the drum (3).
  • the drive (1) for a concrete mixer vehicle comprises a three-stage epicyclic gear, although different embodiments can also be provided having two or four stages.
  • the box (19) of the drive (1) only houses inside (Fig. 3, Fig 4, Fig 10) the first two gear stages of the reduction gear:
  • the third stage of the drive (1) is advantageously positioned on the opposite side of the fixing flange (23) with respect to first and second stage of the drive (1 ) and it comprises planetary-gear support (17) of the third stage, planetary-gears (16) of the third stage and pinion (15) of the third stage.
  • the third stage (15, 16, 17, 21) is advantageously housed inside (Fig. 3) a chamber (26) which is obtained at the head of the drum (3).
  • the hydraulic motor (2) is fixed on the box (19) of the drive (1) in correspondence of the cover (18) which closes the inside of the box (19) containing the first stage (9, 10, 11) and containing the second stage (12, 13, 14) of the drive (1).
  • the shaft (32) of the motor (2) is advantageously (Fig. 3, Fig. 4, Fig. 10) structured so as to integrate in it also the function of the pinion (9) of the first stage and it is supported on the cover (18) by means of a second bearing (31 ).
  • the integration of the pinion (9) of the first stage and of the shaft (32) of the motor into one single component by obtaining directly on the shaft (32) of the motor the gears of the pinion (9) of the first stage, allows to further reduce the overall dimensions of the drive according to the invention and to reduce the number of components necessary for making the drive with a consequent greater simplicity and simplification of the drive itself, a reduction of weight, an increase in reliability and, as a consequence, a reduction of construction and maintenance costs.
  • the pinion (9) of the first stage that is the shaft (32) of the motor (2) configured and structured as pinion (9) of the first stage, couples with corresponding planetary-gears (10) of the first stage which in turn transmit the motion to a planetary gear-support (11) of the first stage by means of sliding on third bearings (27).
  • the planetary gear-support (11) of the first stage in turn transmits the motion to the pinion (12) of the second stage.
  • the pinion (12) of the second stage couples with corresponding planetary-gears (13) of the second stage which in turn transmit the motion to a planetary gear-support (14) of the second stage by means of sliding on fourth bearings (28).
  • the planetary gear-support (14) of the second stage in turn transmits the motion to the pinion (15) of the third stage.
  • the pinion (15) of the third stage couples with corresponding planetary-gears (16) of the third stage which in turn transmit the motion to a ring-gear (21) by means of sliding on fifth bearings (29).
  • the ring-gear (21) puts in rotation the drum (3) of the concrete mixer vehicle (8) through misalignment coupling means (47) which couple to the fixing flange (23) of the drum (3).
  • the planetary gear-support (17) of the third stage is therefore stationary and integral with or fixed to the central body (24) of the drive.
  • a closing shell-guard (20) is fixed to the ring-gear (21) to close the head of the drive (1).
  • the body (46) of the fixed planetary gear-support of the power stage (15, 16, 17, 21 ) is placed in a position at least partially interspersed between the flange (23) and a central body (24) of the drive wherein the central body (24) of the drive is integral with or fixed to the box (19) of the drive (1) and wherein the central body (24) develops from the box (19) developing in a direction directed towards the power stage (15, 16, 17, 21 ) and is inserted radially internally with respect to the fixed planetary gear-support, that is to say, below it supporting it and acting as a weight releasing element from the flange towards the frame by means of the first bearings.
  • This solution allows to considerably retract the planetary gear-support of the third stage (17) which is thus at least partially interspersed between the flange (23) and the central body (24). In this way one obtains a more compact, solid and reliable structure, as well as a better release of the weight of the drum (3) and of its content through the first bearings (30).
  • the pinion (15) of the third stage rotates within a passing-through housing situated within the central body (24), the central body (24) being interspersed between the pinion (15) of the third stage and the fixed planetary gear-support of the power stage (15, 16, 17, 21 ), consisting of the planetary gear-support of the third stage (17).
  • the new geometry of the central body with respect to the prior art solutions along with the new geometry and assembly of the planetary gear-support of the third stage contributes to reducing the overall dimensions of the part of gear-reduction device which is housed inside the drum of the concrete mixer vehicle, with advantages from the point of view of the reduction of the overall dimensions, reduction of weight and reduction of production costs.
  • the need is prevented for complex solutions of the bell coupling joint type to allow the transmission of the rotational motion and at the same time to also allow the reciprocal displacement between the drum and the fixed portion of the drive which is integral with the frame of the concrete mixer vehicle.
  • the releasing of the portion of the weight of the drum (3) which weights down on the drive (1) occurs by means of the flange (23), which releases the weight on the central body (24) of the drive by means of first bearings (30) with the interposition of the planetary gear-support (17) of the third stage, and, as a consequence, the weight is released through the central body (24) on the box (19) down to the support (5) which is installed on the frame (7) of the concrete mixer vehicle (8).
  • the first bearings (30) are shaped to allow (Fig. 1 , Fig. 2, Fig. 13, Fig. 14, Fig. 15, Fig. 16, Fig. 17, Fig. 18) a misalignment by some degrees between the axis of the drive (1) and the axis of the drum (3) of the concrete mixer vehicle (8) by means of a sliding movement with inclination of the base of the flange (23) with respect to the planetary gear-support (17) of the third stage and the central body (24), which are reciprocally integral elements.
  • the maximum allowed misalignment (Fig. 12, Fig. 13, Fig. 17, Fig. 18) is of at least +/-2 degrees, preferably at least +/-4 degrees.
  • the first bearings (30) are roller bearings.
  • the flange (23), the external ring of the first bearings (30) and the joint (22) of the prior art (Fig. 9) are integrated in one single element consisting of the flange (23) itself.
  • the first bearings (30) are integrated in the fixing flange (23) of the drum (3).
  • integral one means that in the flange (23) one obtains the external rolling path of the rollers of the first bearings (30), the term “external” being referred to a radial direction and to the axis of the drive (34).
  • the integration of the first bearings (30) in the flange (23) allows to obtain a greater space for housing the rollers (42, 43) of the first bearings (30) and in this way it allows to use rollers (42, 43) and first bearings (30) having a larger diameter with greater loading capacity, allowing to obtain a lower stress of the first bearings (30) themselves to the advantage of the reliability and duration of the drive;
  • the rolling surface (45) of the rollers (42, 43) of the first bearings (30) which is obtained and integrated in correspondence of the flange (23) is treated to provide said rolling surface (45) with a greater resistance to wear by means, for example, of hardening surface treatments, preferably hardening surface treatments in the form of induction hardening of the flange (23) in correspondence of the external rolling surface (45) of the rollers (42, 43) of the first bearings (30).
  • the integrated first bearings (30) have a diameter definitely larger with respect to the prior art solutions and larger rollers (42, 43) with respect to the bearing of the prior art solutions, said oversizing being translated into a lower specific pressure acting as load on all the components, both the components of the first bearings (30) and the flange (23), allowing to obtain a greater resistance to wear.
  • the solution of drive according to the invention provided with a flange (23) with first bearings (30) integrated in the flange (23) itself has a longer duration with respect to the prior art solutions which use non-integrated components.
  • the main aim of said integration is to cope with the need to reduce as far as possible the overall dimensions of the part of gear-reduction device which is housed in the drum (3) of the concrete mixer vehicle (8).
  • the solution according to the invention one obtains a double advantage with respect to the prior art solutions:
  • the first bearings (30) are roller bearings with two crowns of rolling bodies in the form of first rollers (42) and second rollers (43) housed in a blocking cage (44) wherein the first rollers (42) and the second rollers (43) are placed according to a reciprocally inclined condition with respect to one another within the blocking cage (44).
  • first bearings (30) are provided with rollers having one single crown of rolling bodies. The misalignment can occur (Fig. 1 , Fig. 12, Fig.
  • deviation angles (33) between the axis (34) of the drive (1 ) and the axis (35) of the drum (3) preferably included in a range at least from 2 degrees to +2 degrees, even more preferably in a range at least from -4 degrees to +4 degrees.
  • the flange (23) which is provided with specific coupling means (47) integrated in the flange (23) itself, allows to obtain the misalignment between the axis (34) of the drive (1 ) and the axis (35) of the drum (3) so that the misalignment affects the flange (23) but not the ring- gear (21).
  • the ring-gear (21) is free to rotate to transmit the motion to the flange (23), while the flange (23) although receiving the rotational motion from the ring- gear (21) is able to be subjected to the indicated misalignment.
  • the ring-gear (21) is configured in a different way with respect to prior art solutions such as SU 1364486, in which the ring-gear is rigidly connected to the pinion of the third stage of reduction in such a way that the ring-gear can rotate but cannot undergo any other movement in any other direction because it is always kept in a coaxial condition of alignment with respect to the pinion of the third stage and, therefore, with respect to the body of the drive.
  • the present invention relates to a drive (1) for the drum (3) of a concrete mixer vehicle (8) comprising a multistage epicyclic gear-reduction device which comprises at least two reduction stages of which:
  • the first reduction stage (9, 10, 11) comprises a power takeoff for the connection of a motor (2)
  • the drive comprises a flange (23) for the fixing or for the final transmission of the motion at the exit of the drive (1) in which the coupling between the power stage (15, 16, 17, 21 ) and the fixing flange (23) occurs by means of coupling means (47) which are configured and structured in such a way as to allow a misalignment between one axis (34) of the drive (1) and one axis (35) of the flange (23) of fixing or final transmission of the output motion.
  • Said misalignment involves the misalignment of the flange (23) with respect to the components of the power stage (15,
  • the power stage (15, 16, 17, 21 ) being configured and structured in such a way as to transmit the rotational motion to the flange (23) in a reciprocal misalignment condition between the first stage of reduction (9, 10, 1 ) and the power stage (15, 16,
  • the coupling means (47) are (Fig. 19) a series elements arranged circumferentially in which each of the coupling means (47) is provided with a coupling interface between the ring-gear (21) and the flange (23) and in which each coupling interface of each of the coupling means (47) is freely oscillating with respect to the other coupling interfaces of the other coupling means (47) of the series.
  • the coupling means (47) are fixed (Fig. 19, Fig. 22) on the flange (23), the coupling interface consisting of a tooth (49) protruding circumferentially externally with respect to the flange (23), each tooth (49) being inserted into a corresponding seat (52) obtained on the ring-gear (21) which is provided with a number of seats (52) at least corresponding to the number of the teeth (49).
  • the coupling means (47) are fixed on the ring-gear (21), the coupling interface consisting of a tooth (49) protruding circumferentially internally with respect to the ring-gear (21 ), each tooth (49) being inserted into a corresponding seat (52) obtained on the flange (23) which is provided with a number of seats (52) at least corresponding to the number of said teeth (49).
  • the coupling means (47) are provided with an articulation (50) of the spherical type which allows the oscillation of the coupling interface.
  • the tooth (49) comprises an insert (48) which is inserted within the articulation (50) of the spherical type, the insert (48) constituting an insertion foot of the tooth (49) within the articulation (50), said insertion foot being free to oscillate by means of the articulation (50) of the spherical type.
  • the coupling means (47) are provided with elastic means (51) in correspondence of a fixing interface of the coupling means (47) themselves and the elastic means (51) are preferably made in the form of coned disk springs with preloading.
  • the provided coned disk springs are configured and structured in such a way as to allow the coupling interface to perform an axial movement of extension or penetration with respect to an indentation (53) within which the coupling means (47) are contained so that the coupling means (47) can essentially slide inside with the described axial movement of extension or penetration.
  • the drive (1) is the drive (1) of a drum (3) of a concrete mixer vehicle (8).
  • the box (19) of the drive comprising fixing means (25) to the frame (7) of the concrete mixer vehicle (8).
  • the flange (23) constitutes a fixing interface between the drive (1) and the drum (3).
  • the coupling means (47) are configured and structured in such a way as to allow a misalignment between the axis (34) of the drive (1) and the axis (35) of the , flange (23) of final transmission of the output motion which coincides with the axis of the drum (3).
  • the fixing flange (23) of the drum (3) is rotationally supported by the first bearings (30) radially internally with respect to a radial direction developing with respect to the axis (34) of the drive (1), that is to say, the first bearings (30) which rotationally support the flange (23) are radially internally with respect to a direction corresponding to the radial direction developing from the central axis (34) of the drive (1).
  • the fixing flange (23) of the drum (3) and the first bearings (30) are reciprocally integrated according to such a configuration and structuring that the fixing flange (23) comprises a rolling surface (45) which is intended for the rolling of rollers (42, 43) of the first bearings (30), said rollers (42, 43) being held in position:
  • a blocking cage (44) which is suitable to be fixed on a first component of the components of the power stage (15, 16, 17) radially situated internally with respect to the flange (23), radially internal being referred to a radial direction developing with respect to the axis (34) of the drive (1).
  • the at least one first bearing is concentric to the flange (23) and is placed within a central hole of the flange which is a central hole which is intended to house at least one first part of the power stage (15, 16, 17) comprising the first component of the components of the power stage (15, 16, 17) which is situated radially internally with respect to the flange (23) and which supports the at least one first bearing (30).
  • the ring-gear (21) is provided (Fig. 10) with a circular perimetrical first sealing gasket (40) which seals the internal part of the drive, the perimetrical sealing gasket (40) constituting a sealing between the ring-gear (21) and the fixing flange (23) of the drum (3).
  • a circular perimetrical second sealing gasket (41 ) is provided (Fig. 10) between the fixing flange (23) of the drum (3) and the central body (24) of the drive, said circular perimetrical second sealing gasket (41) constituting a sealing element of the internal part of the drive with respect to the external environment.
  • the fixing flange (23) also constitutes, in addition to the element of fixing of the drive to the drum (3), a sealing element of the drive both with respect to the inside the drum (3) by means of the first sealing gasket (40) and with respect to the external environment by means of the second sealing gasket (41), the first sealing gasket (40) and the second sealing gasket (41 ) being placed on essentially opposite sides of the fixing flange (23) for the sealing of the only two opening portions which may lead to the penetration of dirt in the drive (1 ), besides ensuring the sealing function of the lubricating oil.
  • the fixing flange is integral with or fixed to the drum (3) and as a consequence it is possible to stably protect the zone which could be more subject to stresses and infiltrations because of the oscillations or inclinations of the drum (3) which are allowed by the drive (1) according to the invention by means of the misalignment coupling means (47).
  • the first sealing gasket (40) allows to avoid providing an additional housing of protection of the drive within the volume of the drum (3), with a consequent further simplification of the drive and saving of weight and space in terms of useful volume inside the drum (3).
  • the first sealing gasket (40) is configured and structured to be flexible and deformable within the gap left between the ring-gear (21) and the fixing flange (23) of the drum (3).
  • the ring-gear (21) and the fixing flange (23) are mounted on the drive (1) according to a configuration in which the ring-gear (21) and the fixing flange (23) are reciprocally floating a with respect to each other, to allow the inclination of the drum (3).
  • the first sealing gasket (40) is advantageously mounted between two components, that is to say, the ring-gear (21 ) and the fixing flange (23) which rotate at the same speed, being the ring-gear (21) itself to transmit the motion to the fixing flange (23) of the drum (3), as previously explained.
  • the first sealing gasket (40) is not subject to relative rotational movements with respect to the ring-gear (21) or to the fixing flange (23) and works, thanks to the flexible and deformable configuration and structuring, only in elongation (Fig. 18) and deflection (Fig. 17) with respect to a rest condition (Fig.
  • the first sealing gasket (40) it is possible to use a floating configuration because the first sealing gasket (40) is able to deform in an elastic way in order to adapt to the movements of the floating ring-gear or to the movements of the fixing flange (23) of the drum (3) at the same time providing an effective sealing function for the oil.
  • the power stage (15, 16, 17, 21) is made according to a configuration with fixed planetary gear-support and a floating flange (23), in which the ring-gear (21 ) transmits the rotational motion from the power stage (15, 16, 17, 21 ) to the fixing flange (23) of the drum (3).
  • the ring-gear (21) is located circumferentially outside with respect to the elements of the power stage (15, 16, 17, 21), in such a way that the ring-gear (21) constitutes the casing of the drive.
  • the misalignment coupling means (47) were designed in such a way as to allow the transmission of motion between the ring-gear (21 ) and the flange (23) at the same time allowing (Fig. 23, Fig. 24) offsetting and the possibility of inclination or misalignment of the ring-gear (21) with respect to the flange (23) in a range at least from 2 degrees to +2 degrees, even more preferably in a range at least from -4 degrees to +4 degrees.
  • the solution provides (Fig. 6, Fig. 17, Fig. 18, Fig. 19, Fig. 20, Fig. 21 , Fig. 22) the use of a series of teeth (49) arranged circumferentially and inserted in an articulation (50) of the spherical type which in its turn is kept compressed on the ring- gear (21) by means of elastic means, preferably in the form of coned disk springs.
  • Each of the misalignment coupling means (47) is therefore made up of a tooth (49) which by means of an insert (48) is inserted within an articulation (50) which is inserted within an indentation (53) of the flange (23) by means of elastic means (51) in the form of coned disk springs.
  • the tooth (49) is coupled with the ring-gear (21) within a seat (52) obtained on the ring-gear (21) itself.
  • the elastic means (51 ), preferably in the form of coned disks, serve both as preloading for reducing possible undesired movements during the motion of the concrete mixer vehicle and because the tooth (49) must be able to follow the movements of the ring-gear (21) going inwards and outwards following always the profile of the ring gear while the tilting flange is moving.
  • the coupling gear (38") comprises recesses (37") obtained on the ring-gear (21 ) within which protrusions (36") are inserted of the planetary-gear of the third stage (16) thus realizing a reciprocal coupling gear.
  • the flange (23) is completely floating with respect to the other components of the drive so that the flange (23) has three degrees of freedom, not being constrained in any other point to the elements of the drive itself if not by means of the described couplings (47, 38").
  • an end-stop element (39) is also provided which is obtained in correspondence of a central body (24) of the drive (1).
  • the end- stop element (39) limits the misalignment of the flange (23) with respect to the components of the power stage (15, 16, 17, 21 ) in correspondence of a maximum misalignment position.
  • At least the power stage (15, 16, 17, 21) is located at the opposite side of the first reduction stage (9, 10, 11 ) with respect to the longitudinal position of the fixing flange (23) of the drum (3), the power stage (15, 16, 17, 21) being placed internally to the drum (3) within a chamber (26) obtained at the head of the drum (3), namely in correspondence of the side of the drum (3) which is the opposite side with respect to the side on which there is the intake for the introduction and the taking-out of the content of the drum (3).
  • the coupling between the power stage (15, 16, 17, 21) and the fixing flange (23) of the drum (3) occurs by means of the misalignment coupling means (47) between the axis (34) of the drive (1) and the axis (35) of the drum (3), such misalignment involving the misalignment of the flange (23) with respect to the components of the power stage (15, 16, 17, 21), the power stage (15, 16, 17, 21) transmitting the rotational motion to the flange (23) in a reciprocal misalignment condition of one with respect to the other one in absence of misalignment conditions between the first reduction stage (9, 0, 11) and the power stage (15, 16, 17, 21).
  • the misalignment between the axis (34) of said drive (1) and the axis (35) of said drum (3) is allowed in a bi-directional way, the misalignment being allowed to occur in both directions, with deviation angles (33) between the axis (34) of the drive (1) and the axis (35) of the drum (3) preferably included in a range at least from - 2 degrees to + 2 degrees, even more preferably in a range at least from - 4 degrees to + 4 degrees.
  • the radially internal rolling surface (45) is (Fig. 4, Fig. 10) an essentially ring shaped circular surface.
  • the average diameter (D1) of the ring shaped configuration is distant by a distance (D3) from a development diameter (D2) along which said coupling means (47) develop one after the other forming said series of elements arranged in said circumferential way.
  • the distance (D3) is defined (Fig. 10) with respect to the longitudinal development of the drive (1).
  • the distance (D3) is between 0 e 30 mm, the distance (D3) preferably being 0 mm.
  • the solution according to the present invention allows to obtain an effective releasing of the portion of the weight of the drum of the concrete mixer which weights down on the drive, at the same time allowing a decreasing of the gear itself keeping its reliability unchanged.
  • the function relative to the transmission of the motion from the motor to the drum and the function relative to the release of the weight of the drum of the concrete mixer and its content are reciprocally free. This allows to obtain a drive having reduced weight and size with all the advantages coming from a reduced price, greater reliability and saving of space.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Preparation Of Clay, And Manufacture Of Mixtures Containing Clay Or Cement (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement comprenant un dispositif de réduction d'engrenages épicyclique à étages multiples, le mécanisme d'entraînement comprenant une bride de fixation 23 ou bride de transmission finale du mouvement, le mécanisme d'entraînement étant pourvu de moyens de couplage qui sont configurés et structurés de manière à permettre un désalignement entre un axe du mécanisme d'entraînement et un axe de la bride de fixation ou bride de transmission finale du mouvement au niveau de la sortie du mécanisme d'entraînement.
PCT/EP2015/001563 2014-08-01 2015-07-30 Mécanisme d'entraînement Ceased WO2016015864A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUD2014A000134 2014-08-01
ITUD20140134 2014-08-01

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WO2016015864A1 true WO2016015864A1 (fr) 2016-02-04

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019038096A1 (fr) * 2017-08-24 2019-02-28 Zf Friedrichshafen Ag Mécanisme d'entraînement de tambour mélangeur
US20250340366A1 (en) * 2024-05-03 2025-11-06 The Heil Co. Front-loading and lifting refuse vehicle

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3090258A (en) * 1958-01-31 1963-05-21 Renk Ag Zahnraeder Epicyclic gear transmission with herringbone teeth
US3393584A (en) * 1965-08-11 1968-07-23 Cleff Peter Herbert Epicyclic gears
DE4336393C1 (de) * 1993-10-26 1994-11-10 Bergische Stahlindustrie Sicherung an einer Zahnkupplung
US20080291772A1 (en) * 2007-04-20 2008-11-27 Klaus-Peter Mollhagen Building material mixer
US20090180722A1 (en) * 2006-03-06 2009-07-16 The Timken Company Load sensing wheel end
WO2013045070A1 (fr) * 2011-09-30 2013-04-04 Pmp Pro-Mec S.P.A. Entraînement pour le tambour d'une bétonnière

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3090258A (en) * 1958-01-31 1963-05-21 Renk Ag Zahnraeder Epicyclic gear transmission with herringbone teeth
US3393584A (en) * 1965-08-11 1968-07-23 Cleff Peter Herbert Epicyclic gears
DE4336393C1 (de) * 1993-10-26 1994-11-10 Bergische Stahlindustrie Sicherung an einer Zahnkupplung
US20090180722A1 (en) * 2006-03-06 2009-07-16 The Timken Company Load sensing wheel end
US20080291772A1 (en) * 2007-04-20 2008-11-27 Klaus-Peter Mollhagen Building material mixer
WO2013045070A1 (fr) * 2011-09-30 2013-04-04 Pmp Pro-Mec S.P.A. Entraînement pour le tambour d'une bétonnière

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019038096A1 (fr) * 2017-08-24 2019-02-28 Zf Friedrichshafen Ag Mécanisme d'entraînement de tambour mélangeur
CN110958934A (zh) * 2017-08-24 2020-04-03 Zf 腓德烈斯哈芬股份公司 搅拌滚筒驱动器
US11458650B2 (en) 2017-08-24 2022-10-04 Zf Friedrichshafen Ag Mixing drum drive
US20250340366A1 (en) * 2024-05-03 2025-11-06 The Heil Co. Front-loading and lifting refuse vehicle
US12545504B2 (en) * 2024-05-03 2026-02-10 The Heil Co. Front-loading and lifting refuse vehicle

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