GB1594972A - Planetary gear including a brake device - Google Patents

Planetary gear including a brake device Download PDF

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Publication number
GB1594972A
GB1594972A GB4967777A GB4967777A GB1594972A GB 1594972 A GB1594972 A GB 1594972A GB 4967777 A GB4967777 A GB 4967777A GB 4967777 A GB4967777 A GB 4967777A GB 1594972 A GB1594972 A GB 1594972A
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United Kingdom
Prior art keywords
brake
ring gear
gear
planetary gear
ring
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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.)
Expired
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GB4967777A
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Kockums Industri AB
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Kockums Industri AB
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Filing date
Publication date
Application filed by Kockums Industri AB filed Critical Kockums Industri AB
Priority to GB4967777A priority Critical patent/GB1594972A/en
Publication of GB1594972A publication Critical patent/GB1594972A/en
Expired legal-status Critical Current

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Classifications

    • 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
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion

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

Description

(54) IMPROVEMENTS IN OR RELATING TO A PLANETARY GEAR INCLUDING A BRAKE DEVICE (71) We, KOCKUMS INDUSTRI AB, a Company duly organized under the Laws of Sweden, of 826 00 Söderhamn, Sweden, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- The present invention relates in general to a planetary gear including a brake device and in particular to a planetary gear and brake device in a vehicle transmission for driving a rotary portion by means of a powered shaft by the intermediary of the planetary gear, the shaft being disposed to drive the sun gear of the planetary gear and the ring gear of the planetary gear forming a stationary part of the planetary gear and being connected to a fixed vehicle part.
It is known in the art to power vehicle wheels from, for example, the rear axle gear by the intermediary of a planetary gear disposed in direct association with the wheel hub. Such a normal type planetary gear consists of a sun gear driven by an output shaft from the rear axle gear, the planet carrier being rotatable and connected to the wheel hub, whereas the ring gear is stationary and is connected to a fixed part of the vehicle, for example a fixed drum shaft on which the hub of the wheel is journalled.
According to a conventional solution, the brake device is operative to act between the stationary ring gear (which is connected to the fixed vehicle part) and the rotary planet carrier (which is connected to the wheel hub). In view of the fact that the wheel hub is normally placed axially within and adjacent the planetary gear and the planetary gear is of a highly compact design, it is, for spacesaving purposes, normal in the art to place the brake axially within the wheel hub with the fixed portion of the brake connected to the vehicle frame or chassis, for example the drum shaft and with the rotary portion of the brake, such as the brake disk in disk brakes, connected to the wheel hub. In view of the fact that the brake is in this case mounted between the wheel hub and the fixed vehicle part (and in other words between the stationary ring gear and the planet carrier rotating with the hub), the brake acts at the same ratio as the ratio between the planet carrier and the ring gear, which is considerably less than the total ratio of the planetary gear.
The object of the present invention is, in a planetary gear of the above-described type (that is to say without altering the constructional principle that the ring gear is stationary and that the planet carrier is connected to the hub and driven by the sun gear connected to the shaft) to dispose the planetary gear such that it makes room for a brake device which acts at a greater ratio between the planetary gear and the wheel hub or, more generally, the output portion driven by the planetary gear.
Naturally, it is also conceivable to dispose the brake between the rotary planet carrier and the sun gear. The advantage that the brake acts at a greater ratio (however, the planetary ratio minus 1) must be obtained at the cost of the disadvantage that both of the parts of the brake, that is to say also the reaction force absorbing means of the brake, rotate during operation. If the brake is a hydraulic brake, the hydraulically operated brake pistons and a portion of the hydraulic circuit will also rotate, which is a very great disadvantage.
However, one object of the present invention is to overcome this inconvenience also in that the brake is disposed such that it acts between the sun gear and the fixed portion of the planetary gear.
According to the present invention there is provided a planetary gear including a brake device for a vehicle transmission for driving a rotary part by means of a driven shaft via the planetary gear, the shaft being operative to drive a sun gear of the planetary gear, and a ring gear of the planetary gear forming a stationary reaction member of the planetary gear and being connected by a ring gear frame to a fixed vehicle part, wherein one of the mutually rotary parts of the brake device is connected to the sun gear for rotation at the same speed as the sun gear and the other part is connected to the stationary ring gear and supported in a space which is defined radially inwardly by the sun gear or the shaft and defined radially outwardly by the ring gear, a ring gear extension or a part of the ring gear frame, and which is axially defined on one side by a planet carrier and on the other side by the ring gear frame.
In a vehicle transmission the rotary portion of the brake may include, as a support for this portion, a ring in mesh with an axial inner extension of the sun gear or in mesh with a shaft between the fixed vehicle part on which the wheel hub is journalled and the planet carrier.
The ring gear frame which supports the non-rotary portion of the brake may be provided with a device for actuating the brake, for example a piston and cylinder assembly.
The present invention and its aspects will be more readily understood from the following description of the accompanying drawings, and discussion relating thereto.
In the accompanying drawings: Fig. 1 is an axial section of a conventional design of a planetary gear which forms the end gear for driving a vehicle wheel, and a wheel hub brake; and Fig. 2 is an axial section of a planetary gear and wheel hub brake designed according to the present invention.
In the conventional design according to Fig. 1, reference numeral 1 designates an output shaft driven by the rear axle gear (not shown) of the vehicle, the output shaft being operative, by the intermediary of a planetary gear generally designated 2, to drive a vehicle wheel 3 which is journalled with its hub 4 by means of hub bearings 5, 6 on a drum shaft 7 fixedly connected to the vehicle.
The output shaft 1 supports the sun gear 8 of the planetary gear at its outer end in engagement with a number of planet gears 9 supported by a planet carrier 10 which, by the intermediary of a connection piece 11, is connected to the wheel hub 4 for rotation together therewith. The planetary gears are, in the normal manner, journalled by means ofjournals 12 on planet gear shafts 13.
A ring gear 14 of the planetary gear which surrounds the planetary gear train and engages, with its inner toothing, with the planet gears 9, is connected to the non-rotary drum shaft 7 by the intermediary of a ring gear frame 15 which has a sheath-shaped portion 16 which is spline-connected to (at 17) and axially retained at (at 17') the non-rotary drum shaft 7 and forms a holder for the one hub journal 5.
A hub brake is disposed axially within the hub 4, the hub brake being generally designated 18 and having, in the illustrated embodiment, the form of a disk brake. The brake disk 19 is fixed to an abutment 20 from the hub 4 and the fixed portion 21 of the brake is fixed to the drum shaft 7, this being fixedly connected to the chassis of the vehicle 22.
Thus, in this device, the brake 18 acts between the fixed chassis portion 22 and the wheel hub 4 and hence, as far as the planetary gear is concerned, acts between the stationary ring gear 14 and the rotary planet carrier 10. The brake 18 is placed in a space which is normally easy to provide between the inner side of the hub and the vehicle chassis 22. Naturally, it is possible to dispose the brake directly between the ring gear frame 15 and the adjacent side of the wheel hub 4 or possibly in a radial space between the parts 11 and 14. This requires an increase of the axial distance between the parts 4 and 15 or an increase of the radial distance between the parts 11 and 14, but this would lead to no gain, since the brake would still act at the same ratio as the ratio between the planetary gear frame 10 and the ring gear frame 15, that is to say a ratio of 1:1.
It is also possible to dispose the brake between the unit comprising shaft/sun gear 1, 8 and the planet carrier 10, which can be made possible by an increase of the axial distance between the planetary gear frame 10 and the ring gear frame 15 and by placing a brake disk on the shaft 1 and the reaction force absorbing portion of the brake on the planet carrier 10. However, the advantage which would thereby be gained would be at the cost of the inconvenience that both the reaction force absorbing portion of the brake and the brake disk rotate during operation, one together with the planet carrier 10 and the other together with the sun gear/shaft 8, 1. Then, for the purposes of hydraulic operation of the brake, the brake cylinder or cylinders with their pistons must rotate and a rotary connection for the hydraulic circuit must be provided, this causing problems not least because of the increased risk of oil leakage from the brake system but also because of the fact that the construction will be highly sensitive to disturbances and will be expensive.
The device according to the present invention obviates the above-described inconveniences and realizes a braking effect with the entire ratio of the planetary gear.
Consequently, as is shown in Fig. 2, the brake 1 8a (in the same axial length of the wheel hub 4a as of the hub 4) is placed in a space which has been provided in that the axial distance between the wheel hub 4a and the planet carrier l0a has been increased, and in that the ring gear 14a of ring gear frame ISa has been extended by a portion designated 14a'. This space, which is axially provided between the planet carrier and the ring gear frame, is radially inwardly defined by the shaft la or an extension of the sun gear 8a and axially outwardly by the ring gear 14a and the above-mentioned extension 14a' by the ring gear 14a and the abovementioned extension 14a' by the ring gear axially inwardly or by the ring gear frame 15a axially outwardly.
The brake is shown in the form of a multiple disk brake but could naturally also be in the form of a drum or disk brake.
The rotary portion of the brake consists of a ring 23 mounted on the shaft la, the hub of the ring engaging with the cogs of the extended sun gear or being in spline engagement with the shaft la at 24. At 25 the ring 23 supports a set of annular brake disks or laminae 27, between which are placed nonrotary brake laminae 28 supported in a conventional manner between two annular pressure plates 29, 30 on either side of the laminae set, of which the one plate 29 can be fixed and the other 30 shiftable, and both be non-rotatably supported by the ring gear or its frame (part 14a'). The shiftable pressure plate 30 is actuable for braking by means of an annular piston or an annular set of pistons 31 in cylinder cavities 32 in the ring gear frame 14a. The cylinder (or each cylinder) 32 is connected to a brake fluid line 33 by means of a channel 34 in the ring gear frame. The drum shaft 7a may be of the same design as the drum shaft 7 in the upper half of the drawing but is shown as a slightly modified construction. The brake fluid line 33 may be an axial channel in the drum shaft for connection to a brake line.
However, it should be noted that the ring 23 may be dispensed with. The reason for this is that the inner laminae may in principle engage directly on the sun gear cogs or with splines within the sun gear.
In Fig. 2, the hub 4a, the hub bearing 5a, 6a and the planetary gear bearing 1 2a are shown only schematically, since it is presupposed that these units are of the same design as corresponding units in the upper half of the drawing.
A summary of the above-described embodiment according to the invention shows that the hub 4a with the hub journals 5a, 6a and the ring gear frame 15a have been moved inwardly in relation to the positions of the corresponding units 4, 5, 6 and 15 in Fig. 1, whereas the planet carrier 10a is in the same position as the planet carrier 10 for realizing a space for the brake. Furthermore, the ring gar 14a is extended inwardly in relation to the ring gear 14 in the upper half of Fig. 1 and constitutes an anchorage for the non-rotary outer laminae 28 of the brake which, thus, are tangentially and radially fixed in relation to the fixed portion of the planetary gear (the ring gear-ring gear frame-drum shaft-vehicle chassis 14a, 15a, 7a, 22). Furthermore, the sun gear 8a is extended inwardly in relation to the sun gear 8 and constitutes (possibly by the intermediary of an intermediate portion 23) an anchorage for the inner laminae disks 27 which rotate at the speed of the shaft/sun gear la, 8a, this speed being a ratio faster than the speed of the hub. If the ratio both in Fig. 1 and in Fig. 2 is presupposed to be 6.42, the rotary portion 23, 27 of the brake 1 8a will thus rotate at a speed which is 6.42 times the speed of the hub.
The advantage inherent in the brake device 1 8a according to the invention is, in other words, that the rotary portion 23, 27 of the brake rotates at a speed which is the total ratio of the planetary gear multiplied by the speed of the brake disk 19 in the brake device 18, at the same time as the construction is just as simple (it should be noticed that the brake device 1 8a may also be a disk brake) in that the reaction force absorbing means of the brake constituted by the pressure plates 29, 30, are non-rotatably connected (but axially shiftable for applying the brake) to the ring gear frame 14a and by the intermediary of this ring gear frame to the fixed portion 7a.
In the above-disclosed example, the brake acts, thus, with the entire ratio of the planetary gear, 6.42:1 instead of 1:1. As a result, for the same mean diameter (it should be noted that the mean diameter is generally equal to the mean diameter in a conventionally mounted multiple disk brake) for the brake, a braking force will be required which is 1:6.42 times lower, which can entail, for example, that air instead of oil can be used as the pressure medium for applying the brakes, that so-called spring-actuated brakes can be used, and that wear is reduced. Another advantage is ease of service. In service of the conventional brake 18, all of the parts, apart from possibly the hub bearing 6, must in general be dismantled, whereas in service of the brake 1 8a according to the invention only a lid 35, the sun gear 8a and the planetary gear frame 14a need be dismantled, which entails a considerable simplification.
As has already been mentioned, the brake 1 8a could well be a disk brake, but it also is possible to use other types of brakes (drum brakes). Naturally, the brake device may also be used for braking another rotary vehicle portion than the wheel hub, for example, a shaft driven by the planetary gear by the intermediary of the planet carrier, for example a shaft for a lifting device or other equipment. Thus, the invention is neither restricted to the field of use described above nor to the embodiment of the illustrated constructional parts.
WHAT WE CLAIM IS: 1. A planetary gear including a brake device for a vehicle transmission for driving a rotary part by means of a driven shaft via the planetary gear, the shaft being operative to drive a sun gear of the planetary gear, and a
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (4)

**WARNING** start of CLMS field may overlap end of DESC **. 14a' by the ring gear 14a and the abovementioned extension 14a' by the ring gear axially inwardly or by the ring gear frame 15a axially outwardly. The brake is shown in the form of a multiple disk brake but could naturally also be in the form of a drum or disk brake. The rotary portion of the brake consists of a ring 23 mounted on the shaft la, the hub of the ring engaging with the cogs of the extended sun gear or being in spline engagement with the shaft la at 24. At 25 the ring 23 supports a set of annular brake disks or laminae 27, between which are placed nonrotary brake laminae 28 supported in a conventional manner between two annular pressure plates 29, 30 on either side of the laminae set, of which the one plate 29 can be fixed and the other 30 shiftable, and both be non-rotatably supported by the ring gear or its frame (part 14a'). The shiftable pressure plate 30 is actuable for braking by means of an annular piston or an annular set of pistons 31 in cylinder cavities 32 in the ring gear frame 14a. The cylinder (or each cylinder) 32 is connected to a brake fluid line 33 by means of a channel 34 in the ring gear frame. The drum shaft 7a may be of the same design as the drum shaft 7 in the upper half of the drawing but is shown as a slightly modified construction. The brake fluid line 33 may be an axial channel in the drum shaft for connection to a brake line. However, it should be noted that the ring 23 may be dispensed with. The reason for this is that the inner laminae may in principle engage directly on the sun gear cogs or with splines within the sun gear. In Fig. 2, the hub 4a, the hub bearing 5a, 6a and the planetary gear bearing 1 2a are shown only schematically, since it is presupposed that these units are of the same design as corresponding units in the upper half of the drawing. A summary of the above-described embodiment according to the invention shows that the hub 4a with the hub journals 5a, 6a and the ring gear frame 15a have been moved inwardly in relation to the positions of the corresponding units 4, 5, 6 and 15 in Fig. 1, whereas the planet carrier 10a is in the same position as the planet carrier 10 for realizing a space for the brake. Furthermore, the ring gar 14a is extended inwardly in relation to the ring gear 14 in the upper half of Fig. 1 and constitutes an anchorage for the non-rotary outer laminae 28 of the brake which, thus, are tangentially and radially fixed in relation to the fixed portion of the planetary gear (the ring gear-ring gear frame-drum shaft-vehicle chassis 14a, 15a, 7a, 22). Furthermore, the sun gear 8a is extended inwardly in relation to the sun gear 8 and constitutes (possibly by the intermediary of an intermediate portion 23) an anchorage for the inner laminae disks 27 which rotate at the speed of the shaft/sun gear la, 8a, this speed being a ratio faster than the speed of the hub. If the ratio both in Fig. 1 and in Fig. 2 is presupposed to be 6.42, the rotary portion 23, 27 of the brake 1 8a will thus rotate at a speed which is 6.42 times the speed of the hub. The advantage inherent in the brake device 1 8a according to the invention is, in other words, that the rotary portion 23, 27 of the brake rotates at a speed which is the total ratio of the planetary gear multiplied by the speed of the brake disk 19 in the brake device 18, at the same time as the construction is just as simple (it should be noticed that the brake device 1 8a may also be a disk brake) in that the reaction force absorbing means of the brake constituted by the pressure plates 29, 30, are non-rotatably connected (but axially shiftable for applying the brake) to the ring gear frame 14a and by the intermediary of this ring gear frame to the fixed portion 7a. In the above-disclosed example, the brake acts, thus, with the entire ratio of the planetary gear, 6.42:1 instead of 1:1. As a result, for the same mean diameter (it should be noted that the mean diameter is generally equal to the mean diameter in a conventionally mounted multiple disk brake) for the brake, a braking force will be required which is 1:6.42 times lower, which can entail, for example, that air instead of oil can be used as the pressure medium for applying the brakes, that so-called spring-actuated brakes can be used, and that wear is reduced. Another advantage is ease of service. In service of the conventional brake 18, all of the parts, apart from possibly the hub bearing 6, must in general be dismantled, whereas in service of the brake 1 8a according to the invention only a lid 35, the sun gear 8a and the planetary gear frame 14a need be dismantled, which entails a considerable simplification. As has already been mentioned, the brake 1 8a could well be a disk brake, but it also is possible to use other types of brakes (drum brakes). Naturally, the brake device may also be used for braking another rotary vehicle portion than the wheel hub, for example, a shaft driven by the planetary gear by the intermediary of the planet carrier, for example a shaft for a lifting device or other equipment. Thus, the invention is neither restricted to the field of use described above nor to the embodiment of the illustrated constructional parts. WHAT WE CLAIM IS:
1. A planetary gear including a brake device for a vehicle transmission for driving a rotary part by means of a driven shaft via the planetary gear, the shaft being operative to drive a sun gear of the planetary gear, and a
ring gear of the planetary gear forming a stationary reaction member of the planetary gear and being connected by a ring gear frame to a fixed vehicle part, wherein one of the mutually rotary parts of the brake device is connected to the sun gear for rotation at the same speed as the sun gear and the other part is connected to the stationary ring gear and supported in a space which is defined radially inwardly by the sun gear or the shaft and defined radially outwardly by the ring gear, a ring gear extension or a part of the ring gear frame, and which is axially defined on one side by a planet carrier and on the other side by the ring gear frame.
2. A planetary gear including a brake device as claimed in Claim 1 in a vehicle transmission, in which the sun gear is mounted to the outer end of the rotary part which is in the form of a drive shaft of a vehicle wheel, and the sun gear is operative, by the intermediary of the planet carrier, to drive a wheel hub which is fixedly connected to the planet carrier and is journalled to a part fixedly connected to the vehicle, to which part the ring gear of the planetary gear is non-rotatably connected by means of the ring gear frame, wherein the rotary portion of the brake includes, as a support therefor, a ring in mesh with an axial inner extension of the sun gear or in mesh with the shaft between the fixed vehicle part to which the wheel hub is journalled and the planet carrier.
3. A planetary gear including a brake device as claimed in Claim 2, wherein the ring gear frame which supports the nonrotary portion of the brake is provided with a device for actuating the brake, for example a piston and cylinder assembly.
4. A planetary gear including a brake device substantially as herein described with reference to, and as shown in, Figure 2 of the accompanying drawings.
GB4967777A 1977-11-29 1977-11-29 Planetary gear including a brake device Expired GB1594972A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB4967777A GB1594972A (en) 1977-11-29 1977-11-29 Planetary gear including a brake device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB4967777A GB1594972A (en) 1977-11-29 1977-11-29 Planetary gear including a brake device

Publications (1)

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GB1594972A true GB1594972A (en) 1981-08-05

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GB4967777A Expired GB1594972A (en) 1977-11-29 1977-11-29 Planetary gear including a brake device

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2535254A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE WHEEL HUB
FR2535255A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE WHEEL HUB
FR2535257A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED REDUCER WHEEL HUB
FR2535258A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE AND REDUCER WHEEL HUB
CN114286756A (en) * 2019-09-05 2022-04-05 克诺尔商用车制动系统有限公司 Braking system for a two-wheeled vehicle axle

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2535254A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE WHEEL HUB
FR2535255A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE WHEEL HUB
FR2535257A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED REDUCER WHEEL HUB
FR2535258A1 (en) * 1982-11-03 1984-05-04 Soma Europ Transmissions INTEGRATED BRAKE AND REDUCER WHEEL HUB
US4562903A (en) * 1982-11-03 1986-01-07 So.M.A. Europe Transmissions Wheel hub with integral brake and reducer
US4576256A (en) * 1982-11-03 1986-03-18 So.M.A. Europe Transmissions Societe Nouvelle Mecanique Et Automobile Wheel hub with built-in brake
US4583428A (en) * 1982-11-03 1986-04-22 So.M.A. Europe Transmissions Societe Nouvelle Mecanique Et Automobile Wheel hub with integral planetary speed reducer
US4610331A (en) * 1982-11-03 1986-09-09 So.M.A. Europe Transmissions Societe Nouvelle Mecanique Et Automobile Wheel hub with built-in brake
CN114286756A (en) * 2019-09-05 2022-04-05 克诺尔商用车制动系统有限公司 Braking system for a two-wheeled vehicle axle
CN114286756B (en) * 2019-09-05 2024-05-14 克诺尔商用车制动系统有限公司 Braking system for a two-tire axle

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