EP1632452B1 - Industrial vehicle with cylinder rigidly connected to load moving device - Google Patents

Description

The present invention relates to an industrial truck with a load transfer device, according to the preamble of claim 1.

A generic truck is out of the US 3,362,503 A known.

Especially FIG. 3 of the US 3,362,503 A shows in conjunction with FIG. 2 how a cylinder of a piston-cylinder system for lifting and lowering a load-receiving means of a truck may be formed as a structural component of a lifting mast.

In the following, the state of the art is generally stated:

Industrial trucks are well known in the art. As a load transfer device is a mast, an additional stroke, a side thruster and the like. Into consideration. In many known industrial trucks, the cylinder of the at least one piston-cylinder system is usually articulated at its longitudinal end opposite the piston outlet end on the device part assigned to it. For further support, the cylinder usually penetrates a staggered from the articulation point to the piston outlet end hole die, which is firmly connected to the cylinder associated with the device part.

The perforated die holds the cylinder only roughly in position and thus prevents buckling of the piston-cylinder system with the piston extended far. However, the supporting point of the cylinder on the perforated die is generally not designed to transmit appreciable forces to the cylinder. A relative movement between the punch die and the cylinder along the cylinder longitudinal axis and around it is permitted.

In trucks and the load transfer devices provided to them, which are usually steel framework constructions, is the Stiffness of the load transfer device a key factor in terms of reliability and operating efficiency.
It is therefore an object of the present invention to provide a generic truck, the load transfer device without attachment of other components, ie, while avoiding an increase in weight and additional assembly work, is designed stiff, the cylinder of the piston-cylinder assembly should be as free as possible.

This object is achieved by a truck with all features of claim 1. In an embodiment of an industrial truck according to the invention, the cylinder is rigidly connected to the device part assigned to it, such that torsional moments acting about a torsion axis extending in the cylinder longitudinal direction and / or tensile forces and / or pressure forces substantially acting in the cylinder longitudinal direction and / or about a substantially orthogonal to the cylinder longitudinal direction Bending axis acting bending moments of the device part at least on a longitudinal portion of the cylinder, in particular of the cylinder jacket, are transferable.

Such torsional moments can occur in a load transfer device, for example, when the load transfer device has a side thrust device on which a load in the vehicle side direction is taken with respect to a vehicle longitudinal center plane and accelerates or decelerates the truck with such a recorded load.

Tensile and / or compressive forces can be caused by acting on the load transfer device bending moment, such as when the load, as usual in forklifts and order pickers, is accommodated such that the load center of gravity is spaced from the adjustable device parts. When the load is raised, the distance between the center of gravity of the load to the mounting point of the stand of a mast on the truck frame forms a load arm, so that a bending moment acts on the mast about a bending axis extending essentially in the direction of the conveyor belt.

Due to the rigid connection of the cylinder with its associated device part of the cylinder is part of the steel frame structure of the load transfer device and contributes to the overall rigidity. Due to the increased overall stiffness, the same load results in less deformation than in the prior art. In addition, the increased overall stiffness of the load transfer device leads to an increase in the stimulable at the load transfer device natural vibration frequencies so that the same applied compared to the prior art applied load in addition to the lower deformation also stimulates a higher-frequency vibration of the load transfer device, which due to The higher frequency attenuates faster by internal and external friction, as is the case in the prior art.

It is also advantageous that the piston-cylinder unit is to be provided anyway, and thus the increased overall rigidity of the load transfer device can be realized substantially without mass increase or by omission of the hole matrices even with a concomitant reduction in mass.

The cylinder may be connected to its associated device part such that only a load of torsional moment, tensile and / or compressive force or bending moment from the device part to the cylinder is transferable. For the highest possible overall stiffness of the load transfer device, however, it is advantageous if the cylinder is rigidly connected to the device part such that torsional moment as well as tensile and / or compressive forces as well as bending moments can be introduced into the cylinder by the device part.

A rigid connection of the cylinder with the respective device part is then particularly suitable for force and / or torque transmission, when a relative movement between the cylinder and device part in the direction of action of the force and / or the torque is substantially completely prevented.

As a rule, a rigid connection is designed to transmit forces and moments from each of two components to the other, ie bidirectionally. Such bidirectional transferability of torsional moments, tensile and / or compressive forces or bending moments between the cylinder and the device part will also be the rule in the present invention. It is crucial, however, that such forces and moments are transferable from the device part to the cylinder, since it is primarily a question of, from the outside, i. usually from the recorded load to absorb forces acting on the load transfer device on the load transfer device.

In particular, the cylinder jacket lying between the longitudinal ends of the cylinder is suitable for absorbing torsional moments, tensile and / or compressive forces or bending moments, since it represents a body which is homogeneous over a considerable portion of the cylinder length, which consequently results in a substantially homogeneous material loading, which is the result stressed material less strained.

The longitudinal section of the cylinder, on which due to the rigid connection with its associated device part forces and moments are transferable from the device part, can thus be integrated as additional Torsionsoder / and bending spring and / or as tension and / or pressure rod in the framework construction of the load transfer device ,

For the transmission of forces and moments on the cylinder, this can be directly connected to its associated device part. This means that a cylinder outer surface is directly connected to a surface of the device part by form or material connection. Preferably, at least a portion of the cylinder outer wall is directly welded to the device part in direct connection.

Alternatively or additionally, the cylinder can also indirectly with the device part be connected, ie by a holder or a connecting part which is rigidly connected both to the device part and to the cylinder. Again, to ensure the transmission of force and / or torque from the device part to the cylinder, it can be positively or materially connected to the device part, in particular by welding. Welding represents the simplest possible connection, which allows both the transmission of torsional moments, bending moments and tensile and compressive forces from the device part to the cylinder.

The above-mentioned form-fit can be achieved for example by an interspersed by a cylinder portion opening of a cylinder holder, the cylinder outer contour and the Offnungsinnenkontur are bounded in cross-section by a polygon, a toothing or the like and abut each other. Tensile and compressive forces can be positively transferred by means of a holder penetrated by the cylinder on a protruding in the radial direction of the cylinder outer surface projection, preferably a circumferential projection, between the device part and cylinder.

The transfer of a load from the load transfer device to the cylinder can be ensured that the cylinder at least two in the cylinder longitudinally spaced connection points provided with the associated device part for transmitting torsional forces and / or tensile and / or compressive forces and / or bending moments rigidly connected to the cylinder.

In the cylinder part associated with the device by the load absorbed by the truck load bending moments can be absorbed as Zugoder / and compressive forces from the cylinder, if the at least one piston-cylinder system is provided such that the longitudinal axis of the piston-cylinder system parallel to a Guide shaft is arranged, which of guide elements of the Load displacement device is defined, which guide the device parts in their relative movement along the displacement axis. In this case, the tensile and / or compressive force to be absorbed by the cylinder due to the load-induced bending moment at the load transfer device is the lower, the greater the offset of the longitudinal axis of the piston-cylinder system from the guide axis of a guide arrangement formed by guide elements.

The guide axis of a guide arrangement can be defined by the contact points of a plurality of guide elements of a device part to the other device part, such as by each support point of a guide element on its track a line parallel to the displacement axis is drawn, the puncture points of these lines by a to the normal axis of displacement, form vertices of a polygon circumscribing an area, and the resulting guide axis is a parallel to the axis of displacement through the centroid of the area framed by the polygon.

A load transfer device may well have a plurality of guide axes, for example in the case of a mast, which is usually performed at each side end in the conveyor belt transverse direction for movement along the displacement axis.

A stable configuration at a low cost of the device part associated with the cylinder can be achieved by using a profile carrier running along the displacement axis on the relevant device part. In this case, the manipulation or displacement of the load unaffected by the piston-cylinder system with minimal influence on the field of view of the truck can take place when the cylinder is arranged with its cylindrical longitudinal axis parallel to the profile carrier on the device part, wherein the cylinder longitudinal axis with respect to the profile carrier is offset to the side facing away from a load-carrying means of the truck side.

If one uses the cylinder as in the present invention as a torsion spring, tension rod, pressure rod and / or as a bending spring, the cylinder is exposed to a certain deformation due to the forces and moments acting on it from the device part ago.

In this case, the invention prevents the cylinder deformation inhibits a liquid piston movement of the piston relative to the cylinder by a piston guide means is provided as the only guide a piston movement of the piston relative to the cylinder substantially in the cylinder longitudinal direction at the exit region of the piston from the cylinder on the cylinder head.

More specifically, the piston guide means may be provided on an inner peripheral surface of the cylinder head facing the cylinder center longitudinal axis and abut against an outer peripheral surface of the piston facing away from the cylinder center longitudinal axis. The piston guide means then forms an intermediate layer between the cylinder inner surface and the piston outer surface and can be easily replaced.

A cylinder in which the piston according to the invention is guided out of the cylinder for movement in the cylinder longitudinal direction only in the region of the piston outlet, represents an advantageous embodiment due to the omitted piston guide on the piston longitudinal end permanently immersed in the cylinder and the associated simplifications. By eliminating otherwise usual Guiding the piston on the plunger longitudinal end immersed in the cylinder, the cylinder can be freely designed in large parts of its cylinder jacket. In particular, it need not be cylindrical in shape, but may have any polyhedral outer and inner peripheral surface. Only at the piston outlet end of the cylinder is to ensure the piston guide and a sufficient seal against leakage of hydraulic fluid from the cylinder.

According to the invention, at least one structural component of the device part assigned to the cylinder forms a housing wall section of the cylinder.

Characterized in that a structural component of the cylinder associated with the device part forms a housing wall portion of the cylinder, forming cylinder and device part quasi a single common structural unit whose structural rigidity is higher than if a cylinder as a separate component via brackets would be only indirectly connected to a structural component of the device part. Furthermore, this integral construction can reduce the number of components necessary for producing a device part, such as a stand, with a cylinder provided thereon and reduce the required assembly time.

Thus, the torsional stiffness and possibly also the bending and tensile rigidity of the device part can be increased by the components that expand the structural component around a cylinder, so that smaller or lighter structural components without loss of strength and rigidity are used for the same load compared to the prior art can.

In other words, the structural component of the device part serves to limit a cylinder volume into which the piston can be inserted and out of which it can be pushed out. The cylinder and its associated device part form an integral unit.

In terms of design, this can be achieved by virtue of the fact that the cylinder comprises plate elements which are rigidly connected to one another and to the at least one structural component in order to form a cavity for displaceably receiving the piston. Since the cylinder should preferably serve as a hydraulic cylinder and thus be able to withstand high pressures, it is preferred that the plate elements are welded to the at least one structural component. To simplify the structure and to avoid unnecessarily large dead volumes in the cylinder cavity, the plate elements are preferably flat.

As already described above, the device part assigned to the cylinder can have a profile carrier running essentially along the displacement axis. This profile carrier is particularly suitable as the above-mentioned at least one structural component, since it can form a housing wall section of the cylinder over a sufficient length. The device part assigned to the cylinder preferably has two such profile carriers. In such a case, when the profiled supports are arranged parallel to each other, an existing space between the profiled supports can be completed by attaching the aforementioned plate members to the profiled supports to form a pressure-tight cylinder cavity.

In this case, the plate elements are preferably mounted such that they each span the distance between the two profile carriers, so that four plate elements may be sufficient to provide six side surfaces for a cuboid or basically rhombic cylinder cavity, including the two profile carrier. The cylinder interior facing surfaces of the plate elements and the profile support then form the boundary surfaces of the cylinder interior.

As a result of the fact that, in the abovementioned construction method, one-piece plate elements connect the two profile carriers, as has already been stated above, a obtained particularly torsionally rigid integral cylinder device part assembly, so that the same Torsionsbelastung and the same rigidity of the overall arrangement, the profile support can be made smaller or lighter than in the prior art.

Fig. 1

eine perspektivische Ansicht einer ersten Ausführungsform eines erfindungsgemäßen Flurförderzeugs,

Fig. 2

eine Querschnittsansicht der starren Verbindung des Zylinders des Zusatzhubs mit dem Zusatzhubständer,

Fig. 3

eine Querschnittsansicht durch einen Profilträger des Ständers des Hubgerüsts des Flurförderzeugs von Fig. 1,

Fig. 4

eine perspektivische Ansicht einer zweiten Ausführungsform eines Zusatzhubständers eines erfindungsgemäßen Flurförderzeugs,

Fig. 5

eine Vergrößerung des mit V bezeichneten Ausschnitts von Fig. 4,

Fig. 6

eine Seitenansicht des Zusatzhubständers der zweiten Ausführungsform von Fig. 4 sowie

Fig. 7

eine Vorderansicht des Zusatzhubständers der zweiten Ausführungsform von Fig. 4.

In the following, the present invention will be described in more detail with reference to an embodiment. It shows:

Fig. 1

a perspective view of a first embodiment of a truck according to the invention,

Fig. 2

a cross-sectional view of the rigid connection of the cylinder of Zusatzhubs with the Zusatzhubständer,

Fig. 3

a cross-sectional view through a profile carrier of the stand of the mast of the truck of Fig. 1 .

Fig. 4

a perspective view of a second embodiment of a Zusatzhubständers of a truck according to the invention,

Fig. 5

an enlargement of the section of V designated by Fig. 4 .

Fig. 6

a side view of the Zusatzhubständers the second embodiment of Fig. 4 such as

Fig. 7

a front view of the Zusatzhubständers the second embodiment of Fig. 4 ,

A first embodiment of an industrial truck according to the invention is in Fig. 1 generally designated 10. The truck 10 has a mast 12, a thereto in the direction of the double arrow V movably arranged driver station carrier 14, arranged on the driver's seat carrier 14 side thruster 16 and one at the Side thruster 16 arranged additional stroke 18. The Gabelplatzträger 20 carries the two forks 22 and 24, which serve as a load-handling means of the truck 10.

The additional stroke 18 has two profile supports 26 and 28, which are essentially parallel to one another and extend in the direction of the movement direction V, which contribute to the formation of an auxiliary lifting element 19 and to which the fork carriage 20 is guided for movement in the direction of the double arrow V.

The profile carriers 26 and 28 are arranged in the direction of the width V substantially orthogonal width direction B of the fork carrier 20 at a distance from each other, wherein between the profile beams 26 and 28, a piston-cylinder system 30 is arranged. The piston-cylinder system 30 has a piston or a piston rod 32, which in Fig. 1 completely retracted into a cylinder 34 of the piston-cylinder system 30.

The cylinder 34 of the piston-cylinder system 30 is connected by means of two transverse struts 36 and 38 with the stand 19 belonging to the additional stroke 18 profile carriers 26 and 28. This connection is rigid, wherein both the cylinder outer surface 34a is welded to the transverse struts 36 and 38 and the respective longitudinal ends of the transverse struts 36 and 38 are welded to the profile carriers 26 and 28.

By this type of rigid connection of the cylinder 34 with the stator 19 of the additional stroke torsional moments about the torsion axis T, which can be introduced about dynamically when starting or braking the truck with recorded on the fork carriage 20 load in the stator 19, from the stator 19th be transferred to the cylinder 34. The cylinder 34 then acts as a torsion spring and stiffens the profile carrier 26 and 28 comprehensive stand 19 of the additional stroke 18 in addition. In the Fig. 1 Torsion axis T shown coincides with the longitudinal axis L of the cylinder 34, which is ideally also the longitudinal axis of the piston-cylinder system 30.

Should the fork carriage 20 be lifted very far on the additional lift 18 with the load picked up, a bending moment is introduced into the upright 19 by the load taken and by the distance between its center of gravity and the guideways on the profile girders 26 and 28, which is about a width direction B extending bending axis W acts on the stand 19. Due to the rigid connection of the cylinder 34 with the stator 19 also such a bending moment is transmitted to the cylinder 34, so that the cylinder 34 acts as a bending spring and increases the flexural rigidity of the stator 19. Such a bending moment can be caused dynamically for a short time with a high amount, such as when the truck overruns a threshold when the load is picked up and the auxiliary lift 18 is lifted.

Likewise, the cylinder section 34b lying between the two transverse struts 36 and 38 can serve as a tension and compression rod stiffening the upright 18, which can absorb forces acting on the upright 19 along the cylinder longitudinal axis 34.

Due to the rigid connection of the cylinder 34 with the stator 19 such that torsional moments, bending moments and tensile and compressive forces can be transmitted from the stator 19 to the cylinder 34, can without additional components and thus without mass increase a significant stiffening of the stator 19 of Zusatzhubs 18th can be achieved, which significantly increases the reliability and efficiency of the truck 10.

It should be noted that the piston 32 is provided with a piston guide only in the region of the cylinder head 34 c, for example from the piston outlet end of the cylinder 34 to the lower edge of the upper transverse strut 36. Another piston guide is not provided in the piston-cylinder system 30. As a result, a relatively large distance between the piston outer wall and the cylinder inner wall can be held approximately in the longitudinal section 34b of the cylinder 34 located between the transverse struts 36 and 38. so that a load-related deformation of the cylinder 34 can be allowed without a retraction and / or extension movement of the piston 32 in the cylinder 34 into or out of this would be hindered.

In Fig. 2 is schematically shown a cross section through the stator 19 of the additional stroke 18, wherein the cutting plane is orthogonal to the cylinder longitudinal axis L and the upper cross member 36 passes through.

Guideways 40, 42, 44 and 46 are provided on the profile carriers 26 and 28 on their outer legs 26a, 26b, 28a and 28b, on which guide rollers of the fork carrier 20 for guiding the in Fig. 2 Unroll fork carriage 20, not shown, in the direction of double arrow V. The longitudinal ends 36a and 36b of the transverse strut 36 are welded to the middle limbs 26c and 28c of the profile beams 26 and 28, respectively.

The cross strut 36 has a passage opening 48 which is penetrated by the cylinder 34, the in Fig. 2 for the sake of clarity also not shown. The cross strut 36 is also welded in the region of the through hole 48 with the outer surface 34 a of the cylinder 34, as indicated by a sector of the weld 50.

The compound of the cross member 38 with the profile beams 26 and 28 and with the cylinder 34 is to the in Fig. 2 described transverse strut 36 identical, so that can be dispensed with a separate representation of the cross member 38 with reference to the description of the cross member 36.

In Fig. 3 a profile carrier 50 of the mast 12 is shown, on which the driver's seat carrier 14 is guided for adjustment along the double arrow V. The adjustment direction V is in Fig. 3 as already in Fig. 2 , orthogonal to the drawing plane.

To guide the driver station carrier 14 rolls on the driver's seat 14 to a Roll axis R rotatably mounted guide roller 54 on a guide rail 56 on the profile carrier 50 of the mast 12 from.

It is expressly pointed out that the profile carrier 50 is not the only driver station carrier 14 in the adjustment direction V leading device, but that in the direction of adjustment V substantially orthogonal vehicle transverse direction Q spaced from the profile support 50 another profile support is arranged mirror-symmetrically to the illustrated.

The adjustment force necessary for adjusting the driver position carrier 14 is provided by a further piston-cylinder system 60. On the cylinder 64 projections 66 and 68 are formed, which are welded to the direction away from the driver's seat carrier 14 longitudinal ends of the outer legs 50a and 50b of the profile carrier 50. Thus, the cylinder 64, as before the cylinder 34 of the additional stroke 18, rigidly connected to a profile carrier 50 of the mast 52, so that a torsional moment about the orthogonal to the plane of Fig. 2 oriented torsion axis T ', which coincides with the cylinder longitudinal axis L' of the cylinder 64, is transferable from the profile carrier 50 to the cylinder 64. Likewise, a bending moment parallel to the roller axis R or acting around a bending axis W 'orthogonal to both the roller axis R and the torsion axis T' can be introduced into the cylinder 64 by the profile carrier 50.

Furthermore, the cylinder 64 in the cylinder longitudinal direction L 'spaced apart further projections on which the projections 66 and 68 of Fig. 3 correspond, so that also orthogonal to the plane of the Fig. 3 acting tensile and compressive forces can be introduced at least in a cylinder in the longitudinal direction L 'between the spaced-apart projections cylinder section.

It should be noted that the previously mentioned further profile carrier for guiding the driver's seat carrier is also rigidly connected to another cylinder of another piston-cylinder system.

It is easy to see that the bending moment acting around a bending axis orthogonal to the roller axis R 'and the torsion axis T' can be better supported by the cylinder 64 the greater the distance of the cylinder 64 represented by its cylinder longitudinal axis L 'from the neutral fiber NF of FIG Profile carrier 50 is.

In connection with the FIGS. 4 to 7 In the following, a second embodiment of the present invention will be described. Same components as in the FIGS. 1 to 3 are in the FIGS. 4 to 7 provided with the same reference numerals, but increased by the number 100. The second embodiment of FIGS. 4 to 7 will be described below only insofar as it differs from the first embodiment, which in the FIGS. 1 to 3 is shown and their description is expressly incorporated by reference.

The in Fig. 4 shown cylinder 134 is designed such that it, as already described above, the piston 132 only at the outlet end of the cylinder 134 leads.

The cylinder 134 is formed by a front plate 170, a cover plate 172, which contains the guidance of the piston 132 and the outlet opening of the piston 132 from the cylinder 134, a bottom plate 174 and a in Fig. 4 not shown back plate 176 (s. Fig. 6 ). These mentioned plate elements 170 to 176 are welded to one another and to the profiled supports 126 and 128 of the auxiliary handle 119 such that a closed pressure-tight cavity is formed in the interior of the cylinder 134 apart from the outlet opening of the piston 132. Facing surfaces 126a and 128a of the profiled beams 126 and 128 formed from inexpensive U-profile semi-finished products form boundary walls of the inner volume of the cylinder 134.

In Fig. 5 the piston outlet from the cylinder 134 is shown enlarged.

There it can also be seen how the plate elements 170 and 172 cooperate by welding both together and with the profile beams 126 and 128 to form a pressure-tight cylinder interior 134a.

In Fig. 6 is a side view of Zusatzhubständers 119 with integrally formed cylinder 134 can be seen. The dashed line shows the piston 132 immersed in the cylinder interior 134a. A diameter extension 133 at the submerged longitudinal end of the piston 132 prevents complete expulsion of the piston 132 from the cylinder 134.

In addition to this, the presentation of Fig. 7 directed.

It will be understood by those skilled in the art that the cylinder 134 has a supply port through which fluid can be delivered under pressure into the cylinder interior 134a to push the piston 132 out of the cylinder 134. It is likewise provided to be able to discharge the pressure of the fluid, preferably hydraulic oil, from the cylinder interior 134a in order to allow the piston 132 to be submerged in the cylinder 134.

Claims (10)

1. An industrial truck with a load displacement device which comprises two device parts (19;119), which can be displaced relative to one another substantially along a displacement axis (V), and at least one piston/cylinder system (30;130) for providing a force required for the relative displacement of the device parts (19;119), wherein a piston (32;132) of the piston/cylinder system (30;130) is connected to one of the device parts, and a cylinder (34;134) of the piston/cylinder system (30;130) is provided on the respective other one of the device parts (19; 119),
   wherein at least one structural component (26,28;126,128) of the device part (19;119) associated with the cylinder (34;134) forms a housing wall portion of the cylinder (34;134),
   characterised in that a piston guide means (at 34c; at 172) is provided as the only guide for a piston movement of the piston (32;132) relative to the cylinder (34;134) substantially in the cylinder longitudinal direction (L,L') at the outlet region (at 34c; at 172) of the piston (32;132) from the cylinder (134) on the cylinder head (34c), whereas the longitudinal end (at 133) of the piston (132) permanently immersed in the cylinder inner chamber (134a) is not guided.
2. An industrial truck (10) according to Claim 1,
   characterised in that the cylinder (34,64) is rigidly connected to the device part (12,19) associated therewith in such a way that torques acting about a torsion axis (T) extending in the cylinder longitudinal direction (L,L') and/or tensile and/or compressive forces acting substantially in the cylinder longitudinal direction (L,L') and/or bending moments acting about a bending axis (W,W') extending substantially orthogonally with respect to the cylinder longitudinal direction (L,L') can be transmitted from the device part (12,19) at least to a longitudinal portion (34b) the cylinder (34,64), in particular of the cylinder casing.
3. An industrial truck according to Claim 1 or 2,
   characterised in that the cylinder (34,64) is connected directly and/or indirectly to the device part (12,19) associated therewith by form-locking or by adhesive or cohesive connection, in particular is welded thereto.
4. An industrial truck according to Claim 1,2 or 3,
   characterised in that the cylinder (34,64) is rigidly connected at at least two connection points (at 36 and 38), which are provided at a distance from one another in the cylinder longitudinal direction (L,L'), to the device part (12,19) associated therewith so as to transmit torsional forces and/or tensile and/or compressive forces and/or bending moments to the cylinder (34,64).
5. An industrial truck according to any one of the preceding Claims,
   characterised in that the at least one piston/cylinder system (30,60) is provided in such a way that the longitudinal axis (L,L') of the piston/cylinder system (30,60) is arranged parallel to a guide axis, which is defined by guide elements of the load displacement device (12,14,19,20) which guide the device parts (12,14,19,20) in their relative movement along the displacement axis (V), and is arranged offset with respect to this latter axis.
6. An industrial truck according to Claim 5,
   characterised in that the device part (12,19) associated with the cylinder (34,64) has a profiled support (26,28,50) which extends along the displacement axis (V), wherein the cylinder (34,64) is arranged on the device part (12,19) with its cylinder longitudinal axis (L,L') parallel to the profiled support (26,28,50), wherein the cylinder longitudinal axis (L,L') is offset with respect to the profiled support (26,28,50) towards the side facing away from a load-bearing means (22,24) of the industrial truck (10).
7. An industrial truck according to any one of the preceding Claims, characterised in that the piston guide means is provided on an inner circumferential surface of the cylinder head (34c) facing towards the cylinder longitudinal axis (L,L'), and bears against an outer circumferential surface of the piston (32) facing away from the cylinder axis.
8. An industrial truck according to any one of the preceding Claims, characterised in that the cylinder (134) comprises plate elements (170,172,174,176), preferably flat plate elements (170,172,174,176), which are rigidly connected to one another and to the at least one structural component (126,128), preferably by welding, so as to form a cavity (134a) to accommodate displaceably the piston (132).
9. An industrial truck according to any one of the preceding Claims, characterised in that the device part (119) associated with the cylinder (134) has, as the at least one structural component (126,128), at least one, preferably two, profiled supports (126,128) which extend substantially along the displacement axis (V).
10. An industrial truck according to Claim 9, characterised in that the device part (119) associated with the cylinder (134) has two parallel profiled supports (126,128), wherein the cylinder (134) is formed between the profiled supports (126,128).

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