A DEVICE FOR CONTROL OF OPERATING DEVICE

Abstract: Apparatus for adjusting the driving mode ride height of a vehicle, where the vehicle ride height is adjustable within a first range (20a, 20b) when an integral control device in the vehicle has taken up a parking or marshalling mode, and where the vehicle ride height is adjustable within a second, smaller range (21a, 21b) when said control device has taken up a driving mode.

Description: TITLE: A DEVICE FOR CONTROL OF OPERATING DEVICE AREA OF INVENTION The present patent application relates to an apparatus for adjusting the driving mode ride height of a vehicle having a pneumatic suspension system. BACKGROUND OF THE INVENTION When load-carrying vehicles (LCV.s) are to be loaded and unloaded, they normally come to a loading dock. In order to facilitate and to increase the efficiency of loading and unloading, the height of the loading dock should be adapted to the elevation of the loading platform of the LCV. One way of achieving this adaptation is to construct a loading dock having a variable elevation. Such an approach may be economically feasible with highly utilised loading docks such as goods terminals, where loading and unloading are very frequent. Another method of solving the problem of adapting the height of the dock and the elevation of the LCV loading platform, is to provide regulation of the elevation of the vehicle loading platform. Such an approach has the advantage of allowing adaptation also to loading docks having a fixed height. Such a system is described in e.g. GB 2 237 780. In the above patent application a system is described, where the LCV loading platform is located at a predetermined height when the vehicle is operated in its normal driving mode. When the vehicle is parked for loading and unloading, the elevation of the LCV loading platform is adjustable so as to allow an adaptation of its elevation to the height of the loading dock, thus enabling efficient loading and unloading. When the LCV is to be operated in a normal driving mode again, the original fixed elevation of the LCV loading platform is restored. One problem exhibited by the prior art is that the height level assumed by the LCV loading platform, when restoring the elevation of the LCV loading platform for normal operation of the LCV, after performing height adjustment during loading and unloading, is fixed and cannot be varied. This means that when the vehicle is operated in a normal driving mode, i.e. when the vehicle is not parked or is driven at a speed exceeding a low limit speed, the elevation of the LCV loading platform in most cases cannot be adjusted, and in those cases where the elevation is adjustable, it is adjustable within the same range as the permitted range for loading and unloading. This means in the first case that control possibilities are not available, which is a disadvantage with this type of prior art, and in the second case that the ride height in the driving mode is adjustable within a range where a risk of damage to the load and the LCV exists. It has been determined by tests and calculations, that the aerodynamic properties of an LCV are dependent on the elevation of the LCV loading platform. Such tests and calculations have shown that is preferable, for obtaining an LCV having a lower air resistance and thereby a lower fuel consumption, for the eleva- tion of the LCV loading platform to be as low as possible when the vehicle is operated in a driving mode. Thus, it is an object of this invention to allow, by providing the LCV with a possibility of adjusting the elevation of the LCV loading platform, the vehicle to be operated in the driving mode with a low set driving mode elevation or ride height, thereby reducing the air resistance and the fuel consumption. A second advantage of being able to lower the elevation of the lorry loading platform is, in those cases where the absolute height of the lorry is limited by regulations or accessibility, that a larger loading height can be utilised, thereby improving the financial strength of the LCV. Thus, another object of this invention is, by providing the LVC with a possibility to control the height position of the loading platform, to secure that the LVC can be driven with a low ride height, whereas the LVC can carry further load which improves the economy for the LVC. A further advantage of being able to lower the ride height of the LCV framework is that this lowers the cab instep height, which increases the driver comfort. Thus, it is another object of this invention, by providing the LCV with a possibility of adjusting the ride height of the LCV framework, and thereby that of its loading platform and cab, which are affixed to said framework, to lower the cab instep height, thereby increasing the driver comfort. An LCV loading platform is resiliently suspended by the structure carrying wheel axles and wheels. This means, that when the LCV is operated in the driving mode, the LCV loading platform will oscillate around the height level that the loading platform has assumed in an equilibrium position, when standing still. The amplitude of the loading platform oscillations around its equilibrium position is dependent of the quality of the road, the load weight, the vehicle speed and the characteristics of the loading platform suspension. As discussed above, the loading platform of an LCV is fitted to the wheel- carrying structure by resilient means. Such resilient means display elastic proper- ties within a certain range of expansion and compression. If the resilient means are compressed excessively, said means will act like a rigid connection. Such an excessive compression will occur if the loading platform has been adjusted to an excessively low position when the LCV is operated in a driving mode. This entails that the harmonic oscillation which, when the loading platform elevation is correctly adjusted, occurs around the equilibrium position of the loading surface height level, is replaced by an interrupted oscillation when the resilient means is compressed past its elastic range. When interrupted oscillatory motions take place, large accelerations occur, leading to the load, the resilient means, and the LCV as a whole, being subjected to very high stress forces. If the loading platform is adjusted to an excessively high position, problems will also occur, in that the resilient means may be extended in excess of their elastic range. Also in such cases, an interrupted oscillatory motion occurs, leading to high stress forces on the load, the resilient means, and on the LCV as a whole. Yet another object of this invention is, to provide the LCV with a means of adjusting the elevation of its loading platform, said means allowing adjustment within a first, lager range when the vehicle has taken up a parking or marshalling position, and adjustment within a second, smaller range when the vehicle has taken up a driving mode. This means that adjustment of the ride height will be allowed when the vehicle is in a driving mode, but that the elevation or ride height in this mode can only be adjusted within a range which is not detrimental to either the load or the vehicle. One advantage of allowing the ride height of the vehicle framework and loading platform to be adjusted to as high a level as possible, is that the framework ground clearance increases. This is of importance when the vehicle is driven over bad ground, and when the vehicle is driven across angled ramps and steep structures. Still another object of this invention is, by providing the LCV with a means of adjusting the elevation of the vehicle framework and loading platform, that the driver will be able to selectively adjust the ride height in accordance with various conditions; if the vehicle is to be driven on a flat road, in which case as low a ride height as possible is of interest; or if the vehicle is driven over bad ground or across steep ramps and structures, in which case as high a ride height as possible is of interest. A still further advantage of having the vehicle framework and loading platform adjustable within a first, larger range when the vehicle has taken up a parking or marshalling position, and a second, smaller range when the vehicle has taken up a driving mode is, that the vehicle cardan shaft, which is provided for connecting an output shaft of a transmission arranged in the vehicle to a driving wheel axle, is connected to said driving wheel axle in a certain angular position. When the vehicle is standing still or being driven at low speed, a relatively large deviation from this position is allowable. When the vehicle is driven at a higher speed, only a smaller deviation from this angular position is allowable. As the cardan shaft is carried by the same structure that carries the vehicle loading platform, that is the vehicle framework or frame structure, the elevation of the framework, the frame structure, or the loading platform, must only be adjustable within a smaller range when in the driving mode. It is also an object of this invention, by providing the LCV with a means of adjusting the elevation of its loading platform, said means allowing adjustment within a first, lager range when the vehicle has taken up a parking or marshalling position, and within a second, smaller range when the vehicle has taken up a driving mode, to allow adjustment of the ride height when the vehicle is in the driving mode, at the same time allowing the ride height only to be adjusted within a range that is not detrimental to the cardan shaft and its suspension. SUMMARY OF THE INVENTION In order to achieve the above objects of the invention, an apparatus is suggested, according to claim 1, for adjustment of the driving mode ride height of a vehicle, where the vehicle ride height is adjustable within a first, larger range when an integral control device in the vehicle has taken up its parking or marshalling mode, and where the vehicle ride height is adjustable within a second, smaller range when said control device has taken up its driving mode. In one embodiment of the invention, which is described in claims 3 and 5, pneumatic suspension means arranged on the vehicle are utilised as the means changing the height level of the vehicle, for adjustment of the distance between the wheel axle of the vehicle and the vehicle load-carrying structure, and thereby the elevation of the vehicle loading platform. According to these embodiments, mounting of further height regulation means are avoided, which is space, weight and resource saving. In one embodiment of the invention, which is described in claim 5, measuring means are used for determination of a measurement of the distance between the wheel axle and the load-carrying structure; which means that a more exact control of the elevation of the frame structure and the loading platform can be achieved. According to a further embodiment of the invention, described in claim 17, a control unit is suggested for the adjustment of the distance between a load- carrying structure and at least one wheel axle of a vehicle, where said distance is adjustable within a first, larger range when an integral control device in the vehicle has taken up its parking or marshalling mode, and that the vehicle ride height is adjustable within a second, smaller range when said control device has taken up its driving mode. 'Driving mode ride height' refers to the elevation of the loading platform when the LCV is operated in the driving mode. DESCRIPTION OF EMBODIMENT EXAMPLES The invention will be described in detail below, in connection with reference to the drawings, in which: Fig. 1 is a schematic perspective view of an LCV, Fig. 2 shows a pneumatic suspension means, Fig. 3 shows a measuring means for determining a measurement of the distance between the wheel axle and the frame structure of a vehicle, Fig. 4 is a circuit diagram of the vehicle's pneumatic system, Fig. 5a - 5c shows, schematically, the LCV with the elevation of the loading platform set into two extreme end positions and one intermediate position, Fig. 6 shows the driving mode ride height range in relation to the parking and marshalling ride height range for the LCV, and Fig. 7 shows a control unit for control and setting of the distance between wheel axle and frame structure. Fig. 1 shows, schematically, an LCV 1. The vehicle shown in the figure is a tractor vehicle. The invention may however be utilised on a tractor vehicle as well as on a trailer. The LCV 1 is constructed around a frame structure 2 which is intended a/o to carry the cab 3 of the LCV, the LCV front axle (not shown) and the LCV rear axle 4. The frame structure is also intended for supporting the load- carrying structure of the LCV. According to the inventive thought, the load-carrying structure is preferably comprised of a planar loading platform, as the invention is especially advantageous for use in connection with vehicles equipped with loading height level adjustment for the facilitation of loading and unloading. It is however possible to utilise some other type of load-carrying structure, such as a tipper body, a container transporta- tion device, or a tank body. The frame structure is mainly comprised of two longitudinal girders 5, 6, connected by a number of transversal girders 7, 8. The front axle is suspended by a (not shown) wheel axle suspension. The rear axle 4 is suspended by a wheel axle suspension 9. The wheel axle suspension, which is of a conventional type, is comprised of longitudinal stays 10a, 10b, one on each side of the vehicle, which are affixed to the wheel axle 4, one transversal stay 11 that connects the two longitudinal stays 10a, 10b, vertical V-shaped brackets 12a, 12b connecting the longitudinal stays to the LCV frame structure, and diagonal stays 13, 14, connecting a central portion of the wheel axis 4 to the frame structure 2. Said stays/brackets ascertain that the wheel axle is fixed longitudinally and transversally relative to the vehicle. However, the wheel axle is movable around the pivot points 15a, 15b, 16a, 16b around which an axle parallelogram is formed by the longitudinal stays 10a, 10b and the diagonal stays 13, 14. The suspension of the wheel axle by these stays entails that the wheel axle is movable along an arcuate path. In the area around the normal height level position of the wheel axle relative to the frame structure, the wheel axle moves principally in a plane perpendicular to the extension of the girders. The vertical position of the wheel axle relative to the frame structure can be adjusted by means of height adjustment means. The height adjustment means consist of the pneumatic suspension 17a, 18a of the LCV. The pneumatic suspension will be described in greater detail below, in connection with Fig. 2. Between the wheel axle 4 and the frame structure, distance measurement means 29 are arranged, measuring the distance between wheel axle and frame structure. The distance measurement means is described in greater detail below, in connection with Fig. 3. The pneumatic suspension means 17a, 17b, 18a, 18b each comprise an air bellows 20, made of rubber. The air bellows defines a closed space, together with a bottom structure 24 and a top structure 25 affixed to the bellows. The top structure of the air bellows consists of a bead plate 23, threaded onto the top end of the air bellows and fixed to a bellows plate 21. The bottom structure 24 exhibits a cylindrical section 26. The air bellows is, except when it has attained its maximum extended position, partly rolled up onto the cylindrical section 26. The air bellows is arranged to be rolled off the cylindrical section when the pneumatic suspension means is extended, and to be rolled up onto the cylindrical section when the pneumatic suspension means is compressed. The bottom structure 24 comprises a hollow body, provided to increase the total air content of the air bellows, thereby creating an air spring with enhanced spring characteristics. Inside the air bellows there is a rubber spring cushion 27, for the purpose of absorbing the load and impacts, should the air spring function deteriorate. The total height of the air spring is controlled by filling the air bellows with, or draining the air bellows of, compressed air. For this purpose, the pneumatic spring is provided with a connection 22 to a pneumatic system arranged on the vehicle. Fig. 3 shows a means 29 for measurement of the vehicle ride height, i.e. a height level sensor. This means comprises an angular position sensor 30, a lever 31 connected to the angular position sensor, and a control rod 33, connected by a joint 32. The control rod 33 is in turn connected to the wheel axle 4 via a joint 34. When the pneumatic suspension is filled with or drained of, respectively, compressed air, the elevation of the LCV frame structure is changed, pushing the control rod upwards or downwards, which in turn changes the angular position of the lever 31. The angular position of the lever is sensed by the angular position sensor 30, whereby the distance between wheel axle and frame structure, and thereby the elevation of the vehicle, can be determined. Fig. 4 shows, as a circuit diagram, the function of an apparatus 39 for adjusting the elevation of the vehicle frame structure. The apparatus substantially consists of a pneumatic system 40. An electronic control unit 80, a control unit 90, and height level sensors 81, 82, 83 are connected to the apparatus 39. The pneu- matic system 40 controls the entry and exit of compressed air to the forward, 41, 42, and the rear, 43, 44, 45, 46 air bellows. The pneumatic system comprises a compressed air storage means 47 consisting of a number of compressed air reservoirs. The compressed air storage means 47 is connected to a first valve means 48 via a supply line 49. The first valve means comprises a first 50, a second 51, and a third solenoid valve 52. The second solenoid valve 51 exhibits a first 53, a second 54, and a third port 55, to which lines are connected. A drain line 56 is connected to the first port 53. The drain line leads to the surrounding atmosphere via an air filter 57. The supply line 49 is connected to the second port 54. A first connection line 58 is con- nected to the third port 55, connecting the second solenoid valve 51 to a main line 59. The first solenoid valve 50 is operable between a first position 50a and a second position 50b. The second solenoid valve 51 is operable between a first position 51a and a second position 51b. The third solenoid valve 52 is operable between a first position 52a and a second position 52b. When the second solenoid valve 51 is set to its first position 51a, the second port 54 is connected to the third port 55 by an internal passage in the solenoid valve, whereby the main line 59 is connected to the supply line 49 via the first connection line 58. This means that compressed air can be fed from the compressed air storage means 47 to the main line 59. The first port of the second solenoid valve 51 is blocked when the solenoid valve is in this position, thus no compressed air is drained to the surrounding atmosphere. When the second solenoid valve 51 is set to its second position 51b, the third port 55 is connected to the first port 53 by an internal passage in the solenoid valve, whereby the main line 59 is connected to the drain line 56. This means that compressed air from the main line 59 is released to the surrounding atmosphere via the drain line 56. The second port 54 of the second solenoid valve is blocked when the solenoid valve is in this position, thus no compressed air is allowed to enter the main line from the compressed air storage means 47. The first, 50, and the third, 52 solenoid valves are connected to the main line 59 via a second, 60, and a third, 61, connection line. The first and the third solenoid valves are both designed with two ports 62, 63, 64, 65. When the first solenoid valve 50 is set to its first position 50a, the first port of the first solenoid valve is connected to its second port by an internal passage, whereby an inlet line 66 is connected to the main line 59. Compressed air can then be fed from the main line to the inlet line, via an inlet, to the bellows 43, 44, if a higher pressure exists in the main line than in the bellows 43, 44, which is the case when the main line is in connection with the compressed air storage means 47. If the pressure in the main line is lower than in the bellows 43, 44, which is the case when the main line is in connection with the drain line 56, compressed air is transported from the bellows to the main line. When the first solenoid valve 50 is set to its second position 50b, the first and the second ports of the first valve are blocked, whereby the bellows associated with the first valve are pneumatically isolated from the surroundings. This means that when the first valve is set to this position, compressed air can neither be fed into or be drained out from the bellows. When the third solenoid valve 52 is set to its first position 52a, the first port of the third solenoid valve is connected to its second port by an internal passage, whereby an inlet line 67 is connected to the main line 59. Compressed air can then be fed from the main line to the inlet line, via an inlet, to the bellows 45, 46 associated with the third solenoid valve, if a higher pressure exists in the main line than in the bellows 45, 46, which is the case when the main line is in connection with the compressed air storage means 47. If the pressure in the main line is lower than in the bellows 45, 46, which is the case when the main line is in connection with the drain line 56, compressed air is transported from the bellows to the main line. When the third solenoid valve 52 is set to its second position 52b, the first and the second ports of the third valve are blocked, whereby the bellows associated with the third valve are pneumatically isolated from the surroundings. This means that when the third valve is set to this position, compressed air can neither be fed into or be drained out from the bellows. The main line 59 is provided, besides the connections to the first solenoid valve and the second solenoid valve, with a connection to a second valve means 68. The second valve means 68 controls the flow into and out from the forward air bellows 41, 42. The forward valve means may be arranged so as to allow separate supply to the left hand and right hand bellows. In that case, a set of at least two solenoid valves is needed. As the loading of the front axle is substantially symmetrical, it is sufficient for the valve means to allow simultaneous and identical compressed air supply to the forward bellows. In the embodiment shown in Fig. 4, the second valve means consists of a fourth solenoid valve 69. The fourth solenoid valve comprises a first 70, a second 71, and a third port 72. The fourth solenoid valve is operable between a first 71a, and a second position 71b. When the fourth valve is set to its second position 71b, the second port 71 is connected to the third port 72 by an internal passage in the solenoid valve, which is provided with a restrictor 73. When the solenoid valve is set to this position, the two forward bellows 41 , 42 communicate with each other via inlet lines 74, 75 and the internal passage in the fourth solenoid valve. The first port 70 of the fourth solenoid valve is blocked in this position, allowing compressed air neither to be fed into or to be drained out from the bellows. When the fourth valve is set to its first position 71a, the first port 70 is con- nected to the second and third ports, 71, 72, via internal passages 76 in the solenoid valve. When the solenoid valve is set to this position, the two forward bellows 41, 42 communicate with the main line 59 via inlet lines 74, 75 and the internal passages 76 in the solenoid valve. The first port of the fourth valve is open in this position, whereby air can flow into or out from the bellows in dependence of the setting of the first valve means 48. The solenoid valves comprised in the first and second valve means are operable into their respective first and second positions via signals from a control device 80. The solenoid valves assume, in their non-actuated mode where no current is flowing through a solenoid arranged in each solenoid valve, their respective second positions. The solenoids are biased to this position by a mechanical spring included in each solenoid valve, which holds the solenoid valve in its second position. When a current flows through the solenoid arranged in each solenoid valve, a magnet core provided inside the solenoid compresses the mechanical spring, whereupon the solenoid valve assumes its first position. Height level sensors 81, 82, 83 are connected to the control device 80, supplying said means with information about the position of each air bellows. Thereby, the elevation of the LCV may be determined. The control device then controls the position of each of the valve means, or solenoid valves, so as to set and maintain, respectively, the desired elevation of the vehicle. The control device comprises memory cells where limit values for a larger range 20a, 20b, and a smaller range, 21a, 21b, are stored. Furthermore, a factory set default position 20c is also stored. The factory set position can be resumed by setting the control unit to a default position. The size of the larger range is determined, in the case of the invention being utilised for a vehicle having a pneumatic suspension, substantially by the maximum stroke of the air bellows. The size of the smaller range is determined by that range within which the elevation can be maintained without causing damage to the vehicle when operated in the driving mode. The number of devices for adjusting the loading platform elevation is pref- erably three. In the case of three elevation adjustment devices being used, they are preferably arranged in such a manner that one device controls the front end of the LCV, one controls the LCV rear left section and one controls the LCV rear right section. In this manner, a level control can be achieved in such a way that the loading platform remains in a horizontal plane, even if the LCV is loaded with a load weighing more heavily on one side of the LCV. Figs. 5a to 5c show the LCV seen from behind, with the device for adjustment of the loading platform elevation set to one intermediate position and two extreme end positions. In Fig. 5a, the loading platform 2 assumes an intermediate position, from which it may be raised as well as lowered. In Fig. 5b, the device for adjustment of the loading platform elevation has been set for the loading platform to assume its absolutely lowest position. In this position there is no possibility of downwards resiliency by compression of the elevation adjustment device. This means that such an extreme position cannot be utilised when the LCV is in the driving mode, as the loading platform in this case is only resiliency suspended for movement towards a higher elevation of the loading platform. In Fig. 5c, the device for adjustment of the loading platform elevation has been set for the loading platform to assume its absolutely highest position. In this position there is no possibility of upwards resiliency by extension of the elevation adjustment device. This means that such an extreme position cannot be utilised when the LCV is in the driving mode, as the loading platform in this case is only resiliently suspended for movement towards a lower elevation of the loading platform. The ride height 100 designates the distance from the load-carrying frame structure to the ground level 101. Fig. 6 shows an example of within what ranges the elevation may be adjusted, when the vehicle is parked, or, alternatively, is marshalling, i.e. when the vehicle is conducted at a speed below 10-20 km/h. When the vehicle is parked or being marshalled, the elevation may be adjusted between the lowest level 20a and the highest level 20b. The distance between these two levels is typically about 30 cm. This means that the loading platform may be adjusted between an elevation of about 75 cm above ground level and an elevation of about 105 cm above ground level. When the control unit has assumed its driving mode, i.e. preferably when the vehicle is operated in the driving mode, i.e. when the vehicle is not parked, or is driven at a speed exceeding about 20 km/h, the elevation is adjustable between a lowest level 21a and a highest level 21b. The distance between these two levels is typically about 10 cm. This means that the loading platform may be adjusted between an elevation of about 80 cm above ground level and an elevation of about 90 cm above ground level. Fig. 7 shows a control unit 90 for operation and adjustment of the distance between wheel axle and frame structure. The control unit comprises means for adjustment of the size of said distance and selector means for switching the control unit 80 into a driving mode or a parking/marshalling mode. The control unit 90 comprises a first 91, a second 92, a third 93, and a fourth switch 94. The first switch can be switched between a first 95, a second 96, and a third position 97. When the switch is set to its first position 95, the elevation of the LCV loading platform is adjustable within the first, larger range 20a, 20b. This corresponds to the control unit being set to its parking or marshalling mode. When the switch is set to its second position 96, the control unit will assume its driving mode, and the vehicle will assume its preset ride height of the loading platform and the frame structure. When the switch is set to its third position 97, the ride height is adjustable within the second, smaller range 21a, 21b. The third switch 93 can be switched between a first position 98, a second position 99, and a neutral position. When the third switch 93 is set to its first position 98, the desired elevation is increased. When the third switch 93 is set to its second position 99, the desired elevation is decreased. When the third switch 93 is set to its neutral position, the first and the second valve means will assume such positions as to allow neither compressed air into or out from the pneumatic suspen- sion means. This means that the first, the third and the fourth solenoid valve 50, 52, 69 are all set to their respective second positions 50b, 52b, 71b. The elevation adjustment, i.e. the setting of the desired height level of the loading platform, and of the size of the desired distance between the wheel axle and the frame structure, respectively, within the smaller range, when the control unit is set into its driving mode, as well as the larger range, when the control unit is set into its parking or marshalling mode, is made by pushing the third switch from its neutral position to either its first position, thereby increasing the set elevation, or to its second position, thereby reducing the set elevation. When the elevation is increased, the second valve means is set to such a mode as to connect the compressed air supply to the main line 59. This means that the second solenoid valve 51 is set to its first position 51a. When the elevation is decreased, the second valve means is set to such a mode as to connect the main line 59 to the drain line. This means that the second solenoid valve 51 is set to its second position 51b. The fourth switch 94 is used to change the control unit switches into other function modes, a/o in order to allow resetting of the default, factory set ride height, to retrieve and program a number of preselected elevations when the control unit is set to its parking or marshalling mode. The second switch 92 may selectively be set into a first 102, a second 103, or a third position 104. When the second switch 92 is set to its first position 102, the first 48, and the second valve means 68 are set in such a manner as to affect only the elevation setting of the front axle. This means that the first and the third solenoid valves 50, 52 are set to their respective second positions 50b, 52b, whereas the fourth sole- noid valve 69 is set to its first position 71a. When the second switch 92 is set to its second position 103, the first 48, and the second valve means 68 are set in such a manner as to affect the elevation adjustment of the front axle and the rear axle, or rear axles, simultaneously. This means that the first and the third solenoid valves 50, 52 are set to their respective first positions 50a, 52a, and the fourth solenoid valve 69 is set to its first position 71a. When the second switch 92 is set to its third position 104, the first 48, and the second valve means 68 are set in such a manner as to affect only the elevation setting of the rear axle or axles. This means that the first and the third solenoid valves 50, 52 are set to their respective first positions 50a, 52a whereas the fourth solenoid valve 69 is set to its second position 71b. The control unit 90 is in signalling connection with the control unit 80. The control unit 90 is detachably arranged in the cab 3 in order to allow for the control unit to be positioned inside or outside the cab 3. The elevation adjustment is preferably performed when the vehicle is parked. Setting of the control device to a driving mode does not mean that the vehicle is operated in a driving mode at present. Setting the control device to a driving mode means that the elevation adjustment can be made within the range appropriate for operating the vehicle in a driving mode. The reference 'LCV shall mean a trailer as well as a tractor vehicle. The reference 'ride height' shall mean the elevation above ground level that the loading platform of an LCV has assumed when the control unit is set to a driving mode. The reference 'marshalling' shall mean that the vehicle is driven at low speed. The reference Operated in a driving mode' shall mean that the vehicle is driven at a speed exceeding a certain limit speed.

Claims: CLAIMS: 1. An apparatus for adjusting the driving mode ride height (100) of a vehicle which is built around a frame structure (2), the apparatus comprising means (39) for adjusting the elevation of the vehicle frame structure (2), and a control unit (80) allowing control of said means (39) for adjusting the elevation of the vehicle frame structure, the control unit (80) being arranged for setting to a driving mode or a parking or marshalling mode, characterised in that the vehicle elevation is adjustable within a first, larger range (20a, 20b) when said control unit (80) is in its parking or marshalling mode, and that the vehicle elevation is adjustable within a second, smaller range (21a, 21b) when said control unit is in its driving mode. 2. The apparatus according to claim 1, characterised in that the means for adjusting the elevation of the vehicle frame structure is comprised by the vehicle's pneumatic suspension (40). 3. An apparatus for adjustment of the distance between a load-carrying structure (2) and at least one wheel axle (4) of a vehicle, the apparatus comprising a control unit (80), pneumatic suspension means (41-46) arranged between the wheel axle (4) and the load-carrying structure (2), the control unit comprising means (90) for setting of the desired size of said distance, said pneumatic suspension means (41-46) being pneumatically connected to a source of compressed air (47) via valve means (48, 68) arranged for controllably allowing, in response to signals from said control unit (80), compressed air to be fed into or drained from said pneumatic suspension means (41-46), thereby expanding or compressing said pneumatic suspension means, whereby the distance between the wheel axle and the load- carrying structure is adjusted, characterised in that the control unit (80) is arranged to be set on one hand into a driving mode, on the other into a parking or marshalling mode, that the desired size of the distance between the wheel axle and the load-carrying structure is adjustable within a first, larger range (20a, 20b) when said control unit is set to its parking or marshalling mode, and that the desired size of the distance between the wheel axle and the load-carrying structure is adjustable within a second, smaller range (21a, 21b) when said control unit is set to its driving mode. 4. The apparatus according to claim 3, characterised in that said apparatus includes measuring means (29) for determining a measurement corresponding to the distance between the wheel axle and the load-carrying structure, and that said distance between the wheel axle and the load-carrying structure is adjustable in such a manner that the measurement determined by the measuring means corresponds to the desired size of said distance. 5. The apparatus according to claim 4, characterised in that the measuring means (29) consists of an angular position sensor (30), arranged for detecting an angular position of a lever (31) connected to the angular position sensor (30), that a control rod (33) is articulately fastened to the lever, that the angular position sensor is fastened either to the frame structure (2) or the wheel axle (4), that the control rod (33) is articulately fastened to either the wheel axle or the frame structure in such a manner that the measuring means defines a connection between the wheel axle and the frame structure whereby, when the distance between the wheel axle and the frame structure is changed through the pneumatic suspension means (41-46) being filled with, or drained of, compressed air, the control rod (33) will be pushed upwards and downwards, respectively, entailing a change in the angular position of the lever (31), that the control unit (80) is arranged to receive the angular value detected by the angular position sensor (30) and that the control unit (80) is arranged to determine the distance between the frame structure and the wheel axle on the basis of said detected angular value. 6. The apparatus according to any one of claims 4-5, characterised in that said pneumatic suspension means (41-46) comprises an air bellows (20) made of a flexible material, that the air bellows, together with a bottom structure (24) and a top structure (25) affixed to the bellows, defines a closed space, that a passage (66, 67, 74, 75) connecting said closed space with said valve means is provided in connection with the top structure (25) or the bottom structure (24), that the pneumatic suspension means (41-46) exhibits a cylindrical section (26), that the air bellows is, except when it has attained its maximum extended position, partly rolled up onto the cylindrical section, that the air bellows is arranged to be rolled off the cylindrical section when the pneumatic suspension means is extended, and that the air bellows is arranged to be rolled up onto the cylindrical section when the pneumatic suspension means is compressed. 7. The apparatus according to claim 6, characterised in that the cylindrical section is provided in connection with the bottom structure, which is fastened to the wheel axle, and that the cylindrical section is designed as a hollow body in order to increase the volume of the closed space. 8. The apparatus according to any one of claims 3-7, characterised in that a selector means (90) is connected to the control unit (80), said selector means being arranged for manual setting into a first and a second position, that the control unit is set to its parking or marshalling mode when the selector means is set to its first position, and that the control unit is set to its driving mode when the selector means is set to its second position. 9. The apparatus according to any one of claims 3-7, characterised in that a means for detection of the vehicle speed is associated with the control unit, that the control unit is arranged to be set to its parking or marshalling mode when the vehicle speed falls below a limit value, and that the control unit is intended to be set to its driving mode when the vehicle speed exceeds said limit value. 10. The apparatus according to claim 9, characterised in that said limit value is 0 km/h. 11. The apparatus according to claim 9, characterised in that said limit value is 20 km/h. 12. The apparatus according to any one of claims 3-11 , characterised in that the end positions of the first, larger range are defined by the maximum extension and compression, respectively, of the pneumatic suspension means. 13. The apparatus according to any one of claims 3-11, characterised in that the end positions of the second, smaller range are defined by a maximum and minimum allowable angle of a cardan shaft associated with the vehicle, and by a required upward and downward suspension stroke. 14. A control unit (90), intended for adjusting the distance between a load- carrying structure (2) and at least one wheel axle (4) of a vehicle, the control unit (90) comprising means (92, 93) for setting the desired size of said distance, and a selector means (91) allowing the control unit to be set to a first position and a second position, characterised in that the desired size of the distance between the wheel axle and the load-carrying structure is adjustable within a first, larger range (20a, 20b) when the selector means is set to its first position, and that the desired size of the distance between the wheel axle and the load-carrying structure is adjustable within a second, smaller range (21a, 21b) when the selector means is set to its second position. 15. The control unit according to claim 14, characterised in that said control unit is detachably fitted into a cab structure mounted on the vehicle. 16. The control unit according to claim 14, characterised in that the first position of the selector means corresponds to a parking and marshalling mode of the vehicle, and that the second position of the selector means corresponds to a driving mode of the vehicle. 17. The control unit according to claim 14, characterised in that the selector means consists of a manual switch.

Inventors: BRANDT PER-OLOF, TERBORN BENGT, BRANDT, PER-OLOF, TERBORN, BENGT
Applicants: BRANDT PER OLOF, TERBORN BENGT, VOLVO AB, AB VOLVO, BRANDT, PER-OLOF, TERBORN, BENGT
Application year: 1998
Main classification: B60G17
IPC codes: B60G9, B60G11, B60G17