Running gear provided with a passive hydraulic wheel set steering system for a rail vehicle

Abstract

A running gear for a rail vehicle includes a front and a rear wheel sets, each provided with left and right wheels. A passive hydraulic wheel set steering system includes a control valve hydraulically connected to hydro-mechanical converters for converting motion of each of the wheels towards and away from the median transverse vertical plane. The control valve is movable between a first position in which the front left and right hydro-mechanical converter assemblies are disconnected from the rear left and right hydro-mechanical converter assemblies, and a second position in which each of the front left and right hydro-mechanical converter assemblies is connected to at least a respective one of the rear left and right hydro-mechanical converter assemblies.

Claims

1. A running gear for a rail vehicle, comprising: at least a pair of wheel sets comprising a front wheel set and a rear wheel set respectively on a front side and a rear side of a median transverse vertical plane of the running gear, each of the front wheel set and rear wheel set having a left wheel and a right wheel, respectively on a left side and a right side of a median longitudinal vertical plane of the running gear, and passive hydraulic wheel set steering system comprising: a front left hydro-mechanical converter assembly for converting motion of the left wheel of the front wheel set towards and away from the median transverse vertical plane into hydraulic energy and vice versa, a front right hydro-mechanical converter assembly for converting motion of the right wheel of the front wheel set towards and away from the median transverse vertical plane into hydraulic energy and vice versa, a rear left hydro-mechanical converter assembly for converting motion of the left wheel of the rear wheel set towards and away from the median transverse vertical plane into hydraulic energy and vice versa, a rear right hydro-mechanical converter assembly for converting motion of the right wheel of the rear wheel set towards and away from the median transverse vertical plane into hydraulic energy and vice versa, wherein the passive hydraulic wheel set steering system further comprises a control valve assembly hydraulically connected to the front left, front right, rear left, and rear right hydro-mechanical converter assemblies, the control valve assembly being movable between at least a first position and a second position, the passive hydraulic wheel set steering system being such that in the first position of the control valve assembly the front left and right hydro-mechanical converter assemblies are disconnected from the rear left and right hydro-mechanical converter assemblies so as to allow movements of the left and right wheels of the front wheel set towards or away from the median transverse vertical plane and movements of the left and right wheels of the rear wheel set towards or away from the median transverse vertical plane that are independent from the movements of the left and right wheels of the front wheel set, and wherein in the second position of the control valve assembly, each of the front left and right hydro-mechanical converter assemblies is connected to at least a respective one of the rear left and right hydro-mechanical converter assemblies.

2. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that at least in the first position of the control valve assembly, a motion of one of the left and right wheels of the front wheel set towards the median transverse vertical plane results in a motion of the other of the left and right wheels of the front wheel set away from the median transverse vertical plane, and a motion of one of the left and right wheels of the rear wheel set towards the median transverse vertical plane results in a motion of the other of the left and right wheels of the rear wheel set away from the median transverse vertical plane.

3. The running gear of claim 2, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, a motion of one of the left and right wheels of the front wheel set towards the median transverse vertical plane results in a motion of the other of the left and right wheels of the front wheel set away from the median transverse vertical plane, and a motion of one of the left and right wheels of the rear wheel set towards the median transverse vertical plane results in a motion of the other of the left and right wheels of the rear wheel set away from the median transverse vertical plane.

4. The running gear of claim 3, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, movements of the left, respectively right wheel of the front wheel set towards, respectively away from the median transverse vertical plane result in movements of the left, respectively right wheel of the rear wheel set towards, respectively away from the median transverse vertical plane, movements of the left wheel of the front wheel set away from the median transverse vertical plane result in movements of the left wheel of the rear wheel set away from the median transverse vertical plane, movements of the right wheel of the front wheel set towards the median transverse vertical plane result in movements of the right wheel of the rear wheel set towards the median transverse vertical plane, and movements of the right wheel of the front wheel set away from the median transverse vertical plane result in movements of the right wheel of the rear wheel set away from the median transverse vertical plane.

5. The running gear of claim 3, wherein the passive hydraulic wheel set steering system is such that in the first position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are connected to one another and the rear left and right hydro-mechanical converter assemblies are connected to one another.

6. The running gear of claim 2, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly movements of the left wheel of the front wheel set towards the median transverse vertical plane result in movements of the left wheel of the rear wheel set towards the median transverse vertical plane, movements of the left wheel of the front wheel set away from the median transverse vertical plane result in movements of the left wheel of the rear wheel set away from the median transverse vertical plane, movements of the right wheel of the front wheel set towards the median transverse vertical plane result in movements of the right wheel of the rear wheel set towards the median transverse vertical plane, and movements of the right wheel of the front wheel set away from the median transverse vertical plane result in movements of the right wheel of the rear wheel set away from the median transverse vertical plane.

7. The running gear of claim 2, wherein the passive hydraulic wheel set steering system is such that in the first position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are connected to one another and the rear left and right hydro-mechanical converter assemblies are connected to one another.

8. The running gear of claim 2, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are disconnected from one another and the rear left and right hydro-mechanical converter assemblies are disconnected from one another.

9. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly movements of the left wheel of the front wheel set towards the median transverse vertical plane result in movements of the left wheel of the rear wheel set towards the median transverse vertical plane, movements of the left wheel of the front wheel set away from the median transverse vertical plane result in movements of the left wheel of the rear wheel set away from the median transverse vertical plane, movements of the right wheel of the front wheel set towards the median transverse vertical plane result in movements of the right wheel of the rear wheel set towards the median transverse vertical plane, and movements of the right wheel of the front wheel set away from the median transverse vertical plane result in movements of the right wheel of the rear wheel set away from the median transverse vertical plane.

10. The running gear of claim 9, wherein the passive hydraulic wheel set steering system is such that in the first position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are connected to one another and the rear left and right hydro-mechanical converter assemblies are connected to one another.

11. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the first position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are connected to one another and the rear left and right hydro-mechanical converter assemblies are connected to one another.

12. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are disconnected from one another and the rear left and right hydro-mechanical converter assemblies are disconnected from one another.

13. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, the front left and right hydro-mechanical converter assemblies are connected with one another and the rear left and right hydro-mechanical converter assemblies are connected with one another.

14. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, the front left and rear left hydro-mechanical converter assemblies are connected to one another and the front right and rear right hydro-mechanical converter assemblies are connected to one another.

15. The running gear of claim 1, wherein the passive hydraulic wheel set steering system is such that in the second position of the control valve assembly, the front left and rear right hydro-mechanical converter assemblies are connected to one another and the front right and rear left hydro-mechanical converter assemblies are connected to one another.

16. The running gear of claim 1, wherein the left and right wheels of the front wheel set are supported on a common front wheel axle and the left and right wheels of the rear wheel set are supported on a common rear wheel axle.

17. The running gear of claim 16, wherein at least one of the front wheel axle and rear wheel axle is pivotally connected to a bogie frame of the running gear via a mechanical pivot for pivoting the said one of the front wheel axle and rear wheel axle about a fixed vertical rotation axis.

18. The running gear of claim 16, wherein a bogie frame of the running gear is pivotally connected to the bogie frame of the running gear without a mechanical pivot for pivoting the said one of the front wheel axle and rear wheel axle about a fixed vertical rotation axis.

19. The running gear of claim 1, further comprising a bogie frame supported on the pair of wheel sets by means of a primary suspension.

20. A rail vehicle comprising a plurality of running gears according to claim 1.

Description

BRIEF DESCRIPTION OF THE FIGURES

(1) Other advantages and features of the invention will then become more clearly apparent from the following description of a specific embodiment of the invention given as non-restrictive examples only and represented in the accompanying drawings in which:

(2) FIG. 1 is a diagrammatic illustration of a running gear of a rail vehicle according to a first embodiment of the invention, in a first operating mode;

(3) FIG. 2 is a diagrammatic illustration of the running gear according to the first embodiment of the invention, in a second operating mode;

(4) FIG. 3 is a diagrammatic illustration of a running gear of a rail vehicle according to a second embodiment of the invention, in a first operating mode;

(5) FIG. 4 is a diagrammatic illustration of the running gear according to the second embodiment of the invention, in a second operating mode.

(6) Corresponding reference numerals refer to the same or corresponding parts in each of the figures.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

(7) With reference to FIGS. 1 and 2, a running gear 10, more specifically a bogie, of a rail vehicle comprises a bogie frame 12 supported on a pair of front and rear wheel sets 14, 16 by means of a primary suspension (not shown). The front wheel set 14 and the rear wheel set 16 are located respectively on a front side and a rear side of a median transverse vertical plane 100 of the running gear 10. Each of the front wheel set 14 and rear wheel set 16 comprises a left wheel 18L, 20L and a right wheel 18R, 20R, respectively on a left side and a right side of a median longitudinal vertical plane 200 of the running gear 10, and an axle 22, resp. 24 on which the left and right wheels 18L, 18R, resp. 20L, 20R are mounted (or which can be integral with the left and right wheels). Each axle 22, 24 can be a drive axle or a dead axle.

(8) The bogie 10 is further provided with a passive hydraulic wheel set steering system 26 comprising: a front left hydro-mechanical converter assembly 28L consisting of a single double-acting cylinder for converting motion of the left wheel 18L of the front wheel set 14 towards and away from the median transverse vertical plane 100 into hydraulic energy and vice versa, a front right hydro-mechanical converter assembly 28R consisting of a single double-acting cylinder for converting motion of the right wheel 18R of the front wheel set 14 towards and away from the median transverse vertical plane 100 into hydraulic energy and vice versa, a rear left hydro-mechanical converter assembly 30L consisting of a single double-acting cylinder for converting motion of the left wheel 20L of the rear wheel set 16 towards and away from the median transverse vertical plane 100 into hydraulic energy and vice versa, and a rear right hydro-mechanical converter assembly 30R consisting of a single double-acting cylinder for converting motion of the right wheel 20R of the rear wheel set 16 towards and away from the median transverse vertical plane 100 into hydraulic energy and vice versa.

(9) The passive hydraulic wheel set steering system 26 further comprises control valve assembly 32 which is depicted as a single twelve-port two-position control valve 32 hydraulically connected to the front left, front right, rear left and rear right hydraulic cylinders by means of hydraulic lines. More specifically, each hydraulic cylinder comprises a front and a rear chamber and each chamber is connected by a direct line to one or two of the ports of the control valve 32.

(10) The control valve 32 is movable between a first position depicted in FIG. 1 and a second position depicted in FIG. 2.

(11) In the first position of the control valve 32 in FIG. 1, the front left and right hydraulic cylinders 28L, 28R are isolated from the rear left and right hydraulic cylinders 30L, 30R, and two fully independent hydraulic circuits are formed, namely a front circuit 34F between the two hydraulic cylinders 28L, 28R of the front wheel set 14 and a rear circuit 34R between the two hydraulic cylinders of the rear wheel set 16. More specifically, the front chambers (i.e. the chambers closest to the front of the bogie 10, towards the left in FIG. 1) of the left and right hydraulic cylinders 28L, 28R of the front wheel set 14 are connected to one another, the rear chambers (i.e. the chambers closest to the rear of the bogie 10, towards the right in FIG. 1) of the left and right hydraulic cylinders 28L, 28R of the front wheel set 14 are connected to one another, the front chambers of the left and right hydraulic cylinders 30L, 30R of the rear wheel set 16 are connected to one another and the rear chambers of the left and right hydraulic cylinders 30L, 30R of the rear wheel set 16 are connected to one another. Hence, a motion of one of the left and right wheels 18L, 18R of the front wheel set 14 towards the median transverse vertical plane 100 due to the contact forces between the wheels 18L, 18R and the track results in a coordinated motion of the other of the left and right wheels 18L, 18R of the front wheel set 14 away from the median transverse vertical plane 100, and a motion of one of the left and right wheels 20L, 20R of the rear wheel set 16 towards the median transverse vertical plane 100 results in a motion of the other of the left and right wheels 20L, 20R of the rear wheel set 16 away from the median transverse vertical plane 100

(12) In the second position of the control valve 32 in FIG. 2, the front left and rear left hydraulic cylinders 28L, 30L are connected to one another and disconnected from the front right and rear right hydraulic cylinders 28R, 30R, which are connected to one another. Two independent hydraulic circuits are formed, namely a left circuit 36L for the hydraulic cylinders 28L, 30L on the left side of the median longitudinal vertical plane 200 and a right circuit 36R for the hydraulic cylinders 28R, 30R on the right side of the median longitudinal vertical plane 200. More specifically, the front chambers of the hydraulic cylinders 28L, 30L of the front wheel set 14 and rear wheel set 16 on the left side of the median longitudinal vertical plane 200 are connected with one another, as are the rear chambers of the hydraulic cylinders 28L, 30L of the front wheel set 14 and rear wheel set 16 on the left side of the median longitudinal vertical plane 200. The same applies to the right side. With these connections, the steering motion of the front wheel set 14 is coordinated with the steering motion of rear wheel set 16. Hence, a motion of the wheel 18L of the front wheel set 14 towards (respectively away from) the median transverse vertical plane 100 due to the contact forces between the wheels 18L, 18R and the track results in a coordinated motion of left wheel 20L of the rear wheel set 16 towards (respectively away from) the median transverse vertical plane 100, and a motion of the right wheel 18R of the front wheel set 14 towards (respectively away from) the median transverse vertical plane 100 results in a motion of the right wheel 20R of the rear wheel set 16 towards (respectively away from) the median transverse vertical plane 100.

(13) The control valve 32 is an electrically operated valve connected to a control unit 38, which may receive signals from various sensors 40, e.g. a GPS unit, a lateral accelerometer, a vehicle speed sensor, to switch the control valve 32 between a straight operating mode corresponding to the position of the control valve 32 in FIG. 1 and a tight curve operating mode corresponding to the position of the control valve 32 in FIG. 2.

(14) The passive hydraulic wheel set steering system 26 operates as follows. In the straight operating mode of FIG. 1, the front and rear wheel sets 14, 16 are independent of one another. The front hydraulic circuit 34F allows coordinated movement of the left and right wheels 18L, 18R of the front wheel set 14 about a front imaginary vertical pivot axis located in the median longitudinal vertical plane 200. Similarly, the rear hydraulic circuit 34R allows coordinated movement of the left and right wheels 20L, 20R of the rear wheel set 16 about a rear imaginary vertical pivot axis located in the median longitudinal vertical plane 200 and spaced apart from the front imaginary pivot axis. Because the rotation motion of the front wheel set 14 about the front imaginary vertical pivot axis is independent of the rotation of the rear wheel set 16 about the rear imaginary vertical pivot axis, each wheel set can find its own optimal (slightly over-radial) position in a wide curve.

(15) In the tight curve operating mode, the left circuit 36L enables coordinated motion of the left wheels 18L, 20L of the front and rear wheel sets 14, 16 such that a motion of the front wheel 18L towards (resp. away from) the median transverse vertical plane 100 results in a coordinated motion of the same amplitude of the rear wheel 20L towards (resp. away from) the median transverse vertical plane 100. Similarly, the right circuit 36R enables coordinated motion of the right wheels 18R, 20R of the front and rear wheel sets 14, 16 such that a motion of the front wheel 18R towards (resp. away from) the median transverse vertical plane 100 results in a coordinated motion of the same amplitude of the rear wheel 20R towards (resp. away from) the median transverse vertical plane 100. However, the left and right circuits 36L, 36F remain independent, which means that the instantaneous motion of each wheel set 14, 16 can be a combination of a rotation about an imaginary instantaneous vertical pivot axis (which is not necessarily located in the median longitudinal vertical plan 200) and a translation in the longitudinal direction towards or away from the median transverse vertical plane 100. While the number of degrees of freedom is the same in the two modes, the tight curve operating mode provides a coordination between the front and rear wheel sets 14, 16 which ensure that a rotation of the front wheel set 14 in one direction about a vertical axis, caused by the reaction of the wheels rolling on the track, will result in a rotation of the rear wheel set 16 in an opposite direction, which is beneficial in tight curves.

(16) Switching the valve from one operating mode to the other does not compromise the steering performance. In a transition from a straight track or wide curve to a tight curve, the steering system is initially in the straight operating mode and the wheel set are free to pivot in a slightly over-radial position before the control valve 32 is switched to the tight curve operating mode. Once the control valve 32 has been switched to the tight curve operating mode, the subsequent rotations of the front and rear wheel sets are coordinated. In a transition from a tight curve back to a straight track, the two wheel sets 14, 16 return to a straight position before the steering system is switched from the tight curve operating mode back to the straight operating mode.

(17) The running gear 10 illustrated in FIGS. 3 and 4 is similar to the running gear of FIGS. 1 and 2 and reference is made to the description of the structure of the running gear of FIGS. 1 and 2 to avoid duplication. The only difference between both assemblies resides in the control valve assembly 32 and hydraulic lines linking the front left, front right, rear left and rear right hydraulic cylinders 28L, 28R, 30L, 30R. The control valve assembly 32 consists of a single four-port two-position or three-position control valve, which is connected to the rear chambers of the two hydraulic cylinders 28L, 28R of the front wheel set 14 and to the front chambers of the two hydraulic cylinders 30L, 30R of the rear wheel set 16. The front chambers of the left and right hydraulic cylinders 28L, 28R of front wheel set 14 are permanently connected with one another. Similarly, the rear chambers of the left and right hydraulic cylinders 30L, 30R of rear wheel set 16 are permanently connected with one another.

(18) The control valve 32 is movable between a first position depicted in FIG. 3 and a second position depicted in FIG. 4.

(19) In the first position of the control valve 32 in FIG. 3, the front left and right hydraulic cylinders 28L, 28R are isolated from the rear left and right hydraulic cylinders 30L, 30R, and two fully independent hydraulic circuits are formed, which are functionally identical with the circuits FIG. 1, namely a front circuit 34F between the two hydraulic cylinders 28L, 28R of the front wheel set 14 and a rear circuit 34R between the two hydraulic cylinders of the rear wheel set 16.

(20) In the second position of the control valve in FIG. 4, a crossed hydraulic circuit 42 is formed. The rear chamber of the left hydraulic cylinder 28L of the front wheel set 14 is connected with the front chamber of the right hydraulic cylinder 30R of the rear wheel set 16, while the rear chamber of the right hydraulic cylinder 28R of the front wheel set 14 is connected with the front chamber of the left hydraulic cylinder 30L of the rear wheel set 16. As the front chambers of the left and right hydraulic cylinders 28L, 28R of front wheel set 14 are still connected with one another and the rear chambers of the left and right hydraulic cylinders 30L, 30R of rear wheel set 16 are connected with one another, the hydraulic system has only one degree of freedom, i.e. the front and rear wheel sets 14, 16 can only rotate about their respective imaginary vertical pivot axis in opposite directions.

(21) The control valve 32 can be operated between a straight operating mode, which corresponds to the position of the control valve 32 in FIG. 3 and is identical with the straight operating mode discussed in connection with FIG. 1, and a tight curve operating mode, which corresponds to the position of the control valve 32 in FIG. 4.

(22) In the tight curve operating mode, the direct connection between the front chambers of the left and right hydraulic cylinders 28L, 28R of the front wheel set 14 ensures that a motion of the left wheel 18L of the front wheel set 14 towards (respectively away from) the median transverse vertical plane 100 will result in a motion of the same amplitude of the right wheel 18R of the front wheel set 14 away from (respectively towards) the median transverse vertical plane 100. Accordingly, the motion of the front wheel set 14 is necessarily a rotation motion about a front imaginary vertical pivot axis located in the median longitudinal vertical plan 200. Similarly, the motion of the rear wheel set 16 is necessarily a rotation motion about a rear imaginary vertical pivot axis located in the median longitudinal vertical plan 200. The motions of the front and rear wheel sets 14, 16 are coordinated and opposed, i.e. a rotation of the front wheel set 14 in one direction will result in a rotation of the rear wheel set 16 in the opposite direction.

(23) While the above examples illustrate preferred embodiments of the present invention it is noted that various other arrangements can also be considered.

(24) As a variant of the first embodiment, one of the wheel sets may be mechanically connected to the bogie frame via a mechanical pivot connection, which defines a fixed vertical pivot axis. This fixed pivot axis does not modify the behaviour of the steering system in the straight operating mode, but prevent translation motions of the wheel sets in the tight curve operating mode. It is not necessary to provide one mechanical pivot connection for each wheel set, since the motion the front and rear wheel sets 14, 16 in the tight curve operating mode are hydraulically coordinated.

(25) The control valve 32 can be mechanically or hydraulically operated, e.g. via an inertia mass allowed to move transversally with respect to the bogie frae 12.

(26) Each hydro-mechanical converter assembly 28L, 28R, 30L, 30R may consist of two single-acting cylinders with or without return spring. They may also consist of piston converters as disclosed e.g. in WO 2007/090825.

(27) The control valve assembly 32 may consist of several valves. The passive hydraulic wheel set steering system 26 may include hydraulic damping means, e.g. restrictions, to stabilise the yawing movement of the wheel sets.

(28) The passive hydraulic wheel set steering system 26 is a passive system insofar as it does not involve a pump for steering the wheel sets 14, 16. This does not mean however, that the hydraulic system has to be hydraulically isolated. A connection to a pump and a tank may be required to compensate leaks in the hydraulic circuits.

(29) The running gear is not necessarily a bogie. The hydro-mechanical converter assembly 28L, 28R, 30L, 30R can for instance be directly fixed to an underframe of a railway carriage, without intermediate bogie frame.

(30) While the passive hydraulic wheel set steering system 26 has been applied to a two-axle bogie, other kinds of running gears may also benefit from it, in particular three-axle bogie with an additional median, non-steerable axle.