瑞典专利SE1251112A1 Control cylinder for a gearbox, a gearbox with such control cylinder, and a vehicle with such a gear

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专利摘要:

公开号:SE1251112A1
申请号:SE1251112
申请日:2012-10-03
公开日:2014-04-04
发明作者:Dieter Slapak
申请人:Scania Cv Ab；
IPC主号:

专利说明:

“IO15202530which are designed in a cylinder housing. A piston in the control cylinder is mounted againstthe inside of the cylinder housing by means of annular body parts, which have recesses for seals.
The seals thus absorb a substantial force according to this embodiment. At the same time mustthe cylinder housing has a considerable length in order to be able to be designed with a sufficientlong bearing surface for the annular body parts.
Document US-A-45 93 606 discloses an operating cylinder for a gearbox for a vehicle.
The control cylinder is equipped with an extra piston, which enables a main piston to be engaged.placed in an intermediate position. The main piston is provided on its outside with a circumferentialplain bearing, which abuts the inside of the cylinder housing. In order for the main piston to be able tostored against the inside of the cylinder housing, the cylinder housing must have a sufficient length.
SUMMARY OF THE INVENTIONDespite known solutions, there is a need to further develop a control cylinder, whichhas a smaller axial extent than existing control cylinders, so that the spacethe need for the control cylinder at the gearbox decreases and so that everyone for the gearboxnecessary components can be fitted to the gearbox.
The object of the present invention is to provide an operating cylinder for onegearbox with small dimensions.
Another object of the invention is to provide a compact control cylinder fora gearbox with low manufacturing cost.
These objects are achieved with an actuating cylinder for a gearbox of it initiallysaid type, which is characterized by the features set forth in claim 1.
A further object of the invention is to provide a gearbox with a maneuverablever cylinder with small dimensions.
“IO15202530This object is achieved with a gearbox which comprises an operating cylinder of the initialsaid type, which is characterized by the features stated in the claim10.
A further object of the invention is to provide a vehicle with a gearboxwith a control cylinder with small dimensions.
This object is achieved with a vehicle which initially comprises a gearbox thereofsaid kind, which is characterized by the features set forth in claim ll.
Such an actuating cylinder has a smaller axial extent than existing actuators.cylinders, which means that the space requirement for the control cylinder at the gearboxdecreases, so that all the components necessary for the gearbox can fit in the gearbox.
Gearboxes for vehicles usually have a number of gear stages, which means ﬂ eracontrol cylinders need to be arranged in the gearbox. Thus, the requirement further increases thateach control cylinder has small dimensions. Due to the fact that thecan be designed with smaller dimensions also reduces the need for materials, whichleads to reduced manufacturing costs of the control cylinder. The gearbox can aswhole is compactly constructed when the control cylinder has small dimensions, whichleads to reduced weight of the vehicle. This also reduces the vehicle's fuel consumption.ning.
Additional advantages of the invention will become apparent from the following detailed description.
BRIEF DESCRIPTION OF THE DRAWINGSIn the following, as an example, a preferred embodiment of the invention is described.one with reference to the accompanying drawings, in which:Pig. 1 shows a schematic side view of a vehicle with an operating cylinder and agearbox according to the present invention,“IO15202530Fig. 2 shows a sectional view of the operating cylinder according to a first embodiment ofthe present invention in a first end position,Fig. 3 shows a sectional view of the operating cylinder according to the first embodiment ofthe present invention in an intermediate position,Fig. 4 shows a sectional view of the operating cylinder according to the first embodiment ofthe present invention in a second end position, andFig. 5 shows a sectional view of the operating cylinder according to a second embodiment ofpresent invention in a first end position.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT OFTHE INVENTIONFig. 1 shows a schematic side view of a vehicle 1, for example a truck. Vehicle 1 isequipped with an internal combustion engine 2, which is connected to a gearbox 4. The gearbox 4is connected to the drive wheel 6 of the vehicle 1 via a propeller shaft 8. The gearbox 4 is provided withan actuating cylinder 10, which has the task of actuating one or more gears 12 in geargearbox 4 in order to change the gearbox through gearbox 4. E ﬁ as gearboxes 4 forVehicle 1 usually comprises a number of gear stages and requires several control cylinders 10is arranged in the gearbox 4. The operating cylinder 10 is preferably of the pneumatic type andaffected by compressed air. However, other ﬂ uids can be used to control the control cylinder10, for example hydraulic oil.
The gearbox 4 in a truck often consists of an automatic gearbox 4, which comprises onelarge number of cooperating components to effect the automatic shifting.
The operating cylinder 10 must therefore be designed as small as possible so that all componentsshall be fitted to the gearbox 4.
Fig. 2 shows a sectional view of the operating cylinder 10 according to a first embodiment of the present invention.present invention in a first end position. The operating cylinder 10 comprises a cylinder“IO15202530house 14, which is provided with a first and second gable 16 resp. 18 to form onespace 20 in which a piston 22 is arranged to be able to be moved axially back and forth.
A piston rod 24 is connected to the piston 22 via a fastening element 26. An opening 28 isarranged in the first end wall 16 through which opening 28 the piston rod 24 is arrangedto stretch. The piston rod 24 is provided at its end facing away from the piston 22 with afastening device 30 for connecting an arm 32, which actuates those present in the gearbox 4give the gears 12 when shifting.
The piston 22 divides it from the cylinder housing 14, the first end 16 and the second end18 forming the space 20 in a first and second space 34 resp. 36. A first port 38communicates with the first space 34 and a second port 40 communicateswith the second space 36. Through the first and second ports 38, 40 access and removala ﬂ uid is moved to surface the piston 22 relative to the cylinder housing 14. The first andthe second ports 38, 40 are connected to a pressure source 42 for ﬂ uid via the first and second valvesvalves 44, 46. The valves 44, 46 are preferably controlled by signals from a control unit 48. Tothe control unit 48 is also connected to a sensor 50, which is mounted in the second end wall18 and which senses the position of the piston 22 in the cylinder housing 14. This is achieved bypartly a pin 52, which is connected to the piston 22, which pin 52 extends into oneelongate recess 54 in the transducer 50. Preferably, the transducer 50 is provided with anot shown coil, which by induction registers where the outer end of the pin 52 is locatedin relation to the coil. By using the sensor 50 sense was in the elongatedIn the recess 54 the pin 52 is located, the position of the piston 22 in the cylinder housing 14 can besued.
A third port 56 is provided in the cylinder housing 14, which third port 56 communicateswith ambient atmospheric pressure. The third port 56 is in contact with a third outlet.space 58, which is formed between the piston 22 and the cylinder housing 14 and a first and a secondradial seal 60 resp. 62, which are arranged between the piston 22 and the cylinder housing 14.
Radial seals 60, 62 are designed to slide on the piston 22 and the cylinder housing 14 atthe axial movement of the piston 22 relative to the cylinder housing 14. The radial seals 60, 62ensures that pressurized ﬂ uid will not be able to flow between the first, second and third1015202530spaces 34, 36, 58. The third gate 56 has the task of leveling anyunderpressure and overpressure to atmospheric pressure in the third space 58.
The first and second radial seals 60, 62 are provided with stiffening elements 64,which are intended to co-operate with a circumferential ﬂ end 68 arranged on the piston 22.
Thus, the radial seals 60, 62 can also act as secondary pistons and transferthe force from the pressurized ﬂ uide on the flange 68 of the piston 22 to thereby exert one onacting axial force of the piston 22.
The piston 22 is provided with an axial bore 70, which is arranged by means of a sliding bearing 72.to abut against a lug 74 arranged on the second end wall 18. The bore 70 haspreferably a substantially circular shape with a center axis 76 as substantiallycoincides with the center axis 78 of the piston 22. Preferably, the lug 74 has a substantiallycircular shape with a diameter smaller than the diameter of the bore 70. Forin the case where both the bore 70 and the lug 74 have a circular shape, the sliding bearing 72 is alsosubstantially circular, so that a stable bearing for the piston 22 is obtained. To the piston 22shall obtain a stable bearing along its entire stroke, the bore 70 and the lug have74 has an axial extent equal to or greater than the stroke of the piston 22. Thethe first end 16 is provided at its opening with a piston rod bearing 80, which togetherman with a piston rod seal 79 stores and absorbs radial forces between the piston roda 24 and the first gable 16. The sliding bearing 72 between the piston 22 and the lug 74 thereonthe second end 18 together with the piston rod bearing 80 causes piston 22 and pistonrod 24 with high stability can be moved back and forth in the cylinder housing 14. Sliding bearing 72between the piston 22 and the lug 74 on the second end wall 18 also means that the operatingThe axial width of the lindem 10 can be reduced, which means that the space requirement forthe operating cylinder 10 at the gearbox 4 decreases, so that all necessary for the gearbox 4components can be fitted to the gearbox 4. Due to the fact that the control cylinder l0 can beformed with smaller dimensions also reduces the need for materials, which leads toincreased manufacturing costs of the control cylinder l0. Gearbox 4 can as a wholeis compactly constructed when the control cylinder l0 has small dimensions, which leadsto reduced weight of the vehicle 1. This also reduces the fuel consumption of the vehicle.ning.1015202530According to the first embodiment of the invention shown in Fig. 2, the sliding bearing 72 is used.arranged in a circumferential recess 82 in the bore 70 of the piston 22.72 to follow the piston 22 in its reciprocating motion. Preferably it iscircumferential recess 82 disposed near an end face 84 of the facing piston 22from the piston rod 24, which results in an increased stability along the entire stroke of the piston 22.
As mentioned above, the actuating cylinder 10 affects the gears in the gearbox 4len 12 when changing. Because the shift is performed from one shift step to another with oneintermediate neutral position, the piston 22 must be steerable to three positions in the cylinder housing14, which correspond to a first and a second end position and an intermediate position.
To move the piston 22 from that of the ﬁ g. 2 shows the first end position of one shown in FIGintermediate position is supplied pressurized id uid both the first and second spaces 34, 36 in the cylinderthe housing 14 through both the first and second ports 38, 40. Thus, the valves 44,46 and pressurized ﬂ uid from the pressure source 42 are supplied to the first and second spaces. Coal-vein 22 will then be displaced to the intermediate position shown in Fig. 3. The radial seals60, 62, which abut against the circumferential ﬂ end 68 of the piston 22, act in part with thethe forces on the piston 22, partly sealing against that formed between the radial seals 60, 62third space 58, so that the pressurized ﬂuide is retained in the first and secondtube 34, 36, and can not reach the third space 58 so as not to be able to leavethe cylinder housing 14 through the third port 56. Preferably, the inside of the cylinder housing 14 isprovided with a circumferential projection 86, which forms abutment surfaces 88 for radial sealing.60, 62. The circumferential projection 86 preferably has an axial extentwhich corresponds to the axial extent of the circumferential ﬂ end 68. By arrangingthe circumferential projection 86 substantially centrally in the cylinder housing 14, it will be shown in FIG.3 is obtained by both the circumferential projection 86 on the cylinderthe housing 14 and the circumferential 68 end 68 of the piston 22 ﬁ are axed between eachradial seal 60, 62. In the intermediate position shown in Fig. 3, the operating cylinder 10 has controlled thein the gearbox 4 existing gears 12 to a neutral position. At the movement of the piston 22 fromthe first position to the intermediate position, the pin 52 has been moved further into the recess 50 of the sensor 5054. The sensor 50 thereby sends signals to the control unit 48 about the position of the piston 22 in the cylindrical position.1015202530housing 14, which means that the control unit 48 can determine which gear is involved.set in gearbox 4. For clarification purposes, control unit 48, valves 44, 46 and pressuresource 42 with associated connections and wires omitted in Fig. 3.
To move the piston 22 from that of the ﬁ g. 3 shows the intermediate position to a second shown in Fig. 4end position is supplied pressurized id uid the first space 34 through the first port 38, togetherearly as the second space 36 is evacuated on ﬂ uid through the second port 40. Forto avoid a negative pressure in the third space 58 will ﬂ uid flow in throughthe third port 56. Thus, the first valve 44 is opened and pressurized ﬂ uid fromthe pressure source 42 is supplied to the first space 34. The second valve 46 ensures that ﬂ uidcan be evacuated through the second port 40. The piston 22 will then be displaced theretosecond end position, shown in ﬁ g. 4. The first radial seal 60 will abutsealing against the circumferential projection 86 in the cylinder housing 14 and preventing pressurizationid uid to reach the third space 58 formed between the radial seals 60, 62, so that itpressurized ﬂ uide is retained in the first space 34, and cannot reach the third space58 so as not to be able to leave the cylinder housing 14 through the third port 56. IIn the intermediate position shown in Fig. 4, the actuating cylinder 10 has controlled those present in the gearbox 4.gear gears 12 to a second gear position. When the piston 22 moves from the intermediate position tothe second end position, the pin 52 has been inserted further into the recess 54 of the sensor 50. The sensorthereby sends signals to the control unit 48 about the position of the piston 22 in the cylinder housing 14. IFor clarification purposes, control unit 48, valves 44, 46 and pressure source 42 with associatedconnections and wires omitted in ﬁ g. 4.
To return the piston 22 to the first end position, the second space 36 is supplied to the second space.whereupon the first and third spaces 34, 58 are evacuated on ﬂ uid. Preferably there is onepassage 90 past the sliding bearing 72, so that ﬂ uid can flow to and from the axial of the piston 22bore 70 via a transverse channel 91 arranged in the second end wall 18, which transversechannel 91 is connected to the second space 36. Thus, the second channelthe tube 36 connects to the axial bore 70 of the piston 22 via the passage 90. Thethe transverse channel 91 extends substantially radially, while the passage 90 extendsextends essentially axially.
Fig. 5 shows a sectional view of the operating cylinder 10 according to a second embodiment ofpresent invention in a first state of mind. What distinguishes the first embodimentfrom the second embodiment is that the sliding bearing 72 is arranged on the lug 74.none of the plain bearings 72 on the lug 74 means that it can be easily disassembled and replacedout by separating the second end wall 18 from the cylinder housing 14 and reassembling itthat a new plain bearing 72 is mounted on the lug 74.
The stated components and features stated above may be within the scope of the inventioncombined between different specified embodiments.

权利要求:
Claims (11)
[1]
An operating cylinder for a gearbox (4), comprising a cylinder housing (14), which is provided with a first and second end (16, 18) to form a space (20), a piston (22), which is provided with a piston rod (24), which piston (22) divides said space (20) into a first and a second space (34, 36); an opening (28) in the first end (16) through which the piston rod (24) is arranged to extend; a first port (38) in communication with the first space (34); and a second port (40) in communication with the second space (36), through which ports (38, 40) a ﬂ uid are supplied and removed to move the piston (22) relative to the cylinder housing (14), in that the piston (22) is provided with an axial bore (70), which by means of a sliding bearing (72) is arranged to abut against a lug (74) arranged on the second end (18).
[2]
Cylinder according to Claim 1, characterized in that the bore (70) has a substantially circular shape with a center axis (76) which substantially coincides with the center axis (78) of the piston (22).
[3]
Cylinder according to Claim 2, characterized in that the lug (74) has a substantially circular shape with a diameter which is smaller than the diameter of the bore (70).
[4]
Cylinder according to one of the preceding claims, characterized in that the bore (70) and the lug (74) have an axial extension which is equal to or exceeds the stroke of the piston (22).
[5]
Cylinder according to one of the preceding claims, characterized in that the plain bearing (72) is substantially circular.
[6]
Cylinder according to one of the preceding claims, characterized in that a third port (56) is arranged in the cylinder housing (14) for removing bort uid from the first and second spaces (34, 36). 10 15 20 11
[7]
Cylinder according to one of the preceding claims, characterized in that a first and a second radial seal (60, 62) are arranged between the piston (22) and the cylinder housing (14), which radial seals (60, 62) are designed to slide on the piston (22 ) and the cylinder housing (14) when the piston (22) moves relative to the cylinder housing (14).
[8]
Cylinder according to one of the preceding claims, characterized in that the plain bearing (72) is arranged in the bore (70) of the piston (22).
[9]
Cylinder according to one of Claims 1 to 7, characterized in that the plain bearing (72) is arranged on the lug (74).
[10]
Gearbox (4), characterized in that it comprises an operating cylinder (10) according to any one of claims 1-9.
[11]
ll. Vehicle (1), characterized in that it comprises a gearbox (4) according to claim 10.

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同族专利:

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引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

DE922211C|1942-09-12|1955-01-10|Westinghouse Bremsen Ges M B H|Hydraulic actuator|

CH319349A|1954-02-27|1957-02-15|Saurer Ag Adolph|Pressure medium-operated servomotor, in particular for switching gears for motor vehicles|

CH446082A|1966-08-15|1967-10-31|Wtz Feikeramischen Ind|Piston actuated by pressure medium, in particular for switching gears for motor vehicles|

DD128820B1|1976-12-21|1980-07-23|Ulrich Bornhoeft|TRIANGULAR CYLINDER FOR TRANSMISSION REMOVAL|

DE3107908A1|1981-03-02|1982-09-16|Leibfried Maschinenbau Gmbh, 7033 Herrenberg|Piston/cylinder unit|

DE3110855C2|1981-03-20|1985-01-03|Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover|Working cylinder with three positions|

US4773300A|1983-10-08|1988-09-27|Wabco Westinghouse Fahrzeugbremsen Gmbh|Three-position working cylinder having dual concentric pistons|

FR2600123B1|1986-06-13|1988-10-07|Renault Vehicules Ind|THREE-POSITION CYLINDER|

DE3820373C2|1988-06-15|1993-10-14|Nlw Foerdertechnik Gmbh|Hydraulic cylinder of short design|

SE504248C2|1995-04-26|1996-12-16|Scania Cv Ab|Gear maneuvering device|

JP3165419B1|1999-12-10|2001-05-14|エスエムシー株式会社|Dual stroke cylinder|

DE102005026475A1|2005-06-09|2006-12-14|Zf Friedrichshafen Ag|vehicle transmissions|

WO2008063104A1|2006-11-22|2008-05-29|Volvo Lastvagnar Ab|Module system for manufacturing two and three stable positions fluid-operated actuators|DE102017002384A1|2017-03-11|2018-09-13|Wabco Gmbh|Piston-cylinder arrangement|

DE102017214526A1|2017-08-21|2019-02-21|Putzmeister Engineering Gmbh|Fluid driven actuator cylinder with an intermediate position and method for actuating such actuator cylinder|

法律状态:

优先权:

申请号 | 申请日 | 专利标题

SE1251112A|SE536688C2|2012-10-03|2012-10-03|Control cylinder for a gearbox, a gearbox with such control cylinder, and a vehicle with such a gearbox|SE1251112A| SE536688C2|2012-10-03|2012-10-03|Control cylinder for a gearbox, a gearbox with such control cylinder, and a vehicle with such a gearbox|

PCT/SE2013/051068| WO2014055008A1|2012-10-03|2013-09-13|Control cylinder for a gearbox, a gearbox with such a control cylinder, and a vehicle with such a gearbox|

DE112013004343.2T| DE112013004343T5|2012-10-03|2013-09-13|Control cylinder for a transmission, transmission with such a control cylinder and vehicle with such a transmission|

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