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Double acting pneumatic cylinders

rodless, with sliding guide, series S5

The rodless cylinders of the S5 series are particularly useful where there is no space for a standard cylinder. The piston rod does not extend from the cylinder. Thanks to their maximum stroke of up to 6 meters, they can also be used in applications where the use of a conventional cylinder would be impossible. This series uses the proven two-strip principle. The S5 series features technopolymer sliding guides on steel guide rods. The carriage can be equipped with a locking unit as an accessory.

Technical information

Technical data

Working pressure	0,6 MPa
Min. pressure	0,3 MPa
Max. pressure	1,0 MPa
Temp. range	-20^oC to +80^oC
Working medium	modified compressed air
Carriage speed	min. 20 mm.s^-1 max. 1,5 m.s^-1

Piston dia.	32	40	50
Force at 0,6 MPa [N]	420	640	1050
Connection	G1/4"	G3/8"	G3/8"
Length of adjustable cushioning [mm]	32,5	41,5	52
Max. stroke [mm]	6000	6000	6000
Stroke tolerance [mm]	+3,2	+3,2	+3,2

For long-term and trouble-free operation, we recommend:
1) speed maximum 1 m.s^-1
2) use a hydraulic shock absorber if the efficiency of the internal cushioning approaches the limit value
3) if the cylinder is used vertically, the cushioning capacity is reduced by 40%
4) maintain a correct and constant lubrication

The pneumatic sealing is achieved through an axial elastomer stripseal reinforced with Kevlar. This system guarantees dimensional stability even with high speeds. The external protection seal consists of a thermoplastic stripseal reinforced with Kevlar.

Weights

Piston dia.	32	40	50
Base weight (0mm) with standard carriage [kg]	2,78	-	-
Base weight (0mm) with medium carriage [kg]	3,27	6,09	10,03
Base weight (0mm) with long carriage [kg]	4,65	8,6	14,04
Weight of 100 mm of stroke [kg]	0,495	0,920	1,280

Construction / materials

caps: ø16: zamak ø25-50: die-cast aluminium
tube: anodized aluminium
piston: aluminium
sliding guide: technopolymer slide, steel guide rods
piston guide slide: acetalic resin
sealings: NBR

Permissible static load and stress

Cylinder force F	Static load			Static moment
Cylinder force F	P1	P2	P3	M1	M2	M3

Piston dia.	F [N] při 0,6 MPa	P1 [N]	P2 [N]	P3 [N]	Standard carriage [Nm]			Medium carriage [Nm]			Long carriage [Nm]
Piston dia.	F [N] při 0,6 MPa	P1 [N]	P2 [N]	P3 [N]	M1	M2	M3	M1	M2	M3	M1	M2	M3
32	420	400	400	400	20	9	27	30	12	40	55	18	75
40	640	600	600	600	-	-	-	60	30	80	110	45	150
50	1050	800	800	800	-	-	-	85	50	110	150	75	210

A moment is the product of the load (N) and the arm (m), i.e the distance between the centre of gravity of the load and the longitudinal axis of the piston. Please note that in dynamic conditions, the load must be reduced due to effects associated with the speed. Calculation of permissible dynamic stress and verification of internal damping efficiency can be found below.

Examination and verification of internal cushioning

In a system with moving masses, as in the case of rodless cylinders, it is essential to control the dissipation of the system’s kinetc energy as it is brought to a stop. First of all, it is necessary to establish and verify the most suitable method for cushioning the system, in order to avoid the moving mass (carriage with load) striking against the end-caps and compromising the life of the cylinder.

If the point corresponding to a given load and speed lies beneath the appropriate curve, the cushioning is able to absorb the kinetic energy of the system. Vice versa if the point lies above the curve, the cushioning is not able to absorbe the kinetic energy. In that case you must:
a) decrease the load and mantain the translation speed
b) decrease the speed and mantain the load
c) select a cylinder with a bigger bore or with twin chambers
d) use external hydtŕaulic shock absorber

Attention: if the cylinder is mounted vertically, the damping efficiency is reduced by 40%.

Dynamic load capacity

Procedure for determining the permissible values for dynamic stress:

determine the KRV coefficient according to the speed

multiply the permissible values for static stress by the KRV coefficient and the value calculated in this way is the maximum permissible value for dynamic stress

Example - verification of the suitability of the cylinder with a misaligned load

Let use suppose that we want to move a load of 50 N displaced at a distance B3 from the central axis, at a maximum translation speed of 1 m/s. Due to the misaligned load a cylinder with an external carriage is required and we must verify if a S5 cylinder dia. 40 mm with integrated slide is suitable for this application.

P3 = 50 N
V = 1 m.s^-1
b2 = 150 mm

b3 = 220 mm

Verification of the cushioning capacity
The graph for verifying the effectiveness of the internal cushioning shows that for a moving mass 5 kg (50 N) and a speed of 1 m.s^-1, the point is under the curve for the diameter 40 mm (but we are already very close to the limit value). This means that the internal damping will be able to absorb energy and safely stop the carriage with the mass, but external hdyraulic shock absorber is recommended.

Calculation and verification of the dynamic load capacity
From the graph for the permissible dynamic load we determine the value of the coefficient KRV. For a speed of 1 m.s^-1 and the S5 series, the value of KRV = 0,11. The value of the permissible dynamic stress CD is the product of the coefficient KRV and the permissible static load CM (here the value P3).
CD = CM · KRV = 600 · 0,11 = 66 N
Since the load P (50 N) is less than the calculated value of CD (66 N), the selected cylinder is suitable for use.

Calculation of dynamic torque
In order to calculate the torques M1, M2 and M3 that act on the carriage, we must calculate the force generated by the load during acceleration and deceleration. We therefore determine the deceleration „a“ at the speed V and the damping length L and the dynamic force F.

Ø	L [mm]
16	16,5
25	25
32	32,5
40	41,5
50	52

a = v²/(2 * L * 10^-3) = 1²/(2 * 41,5 * 10^-3) = 12 m.s^-2

The dynamic force F will then be

F = (P * a)/9,81 = (50 * 12)/9,81 = 61 N

The toquues are then given by the relations:
MD1 = F · b2 = 61 · 150 = 9150 Nmm = 9,2 Nm
MD2 = P · b2 = 50 · 150 = 7500 Nmm = 7,5 Nm
MD3 = F · b3 = 61 · 200 = 12200 Nmm = 12,2 Nm
Since the permissible value of torque M1 (60 Nm) is greater than the calculated value of MD1 (9,2 Nm), the permissible value of torque M2 (30 Nm) is greater than the calculated value of MD2 (7,5 Nm) and the permissible value of torque M3 (80 Nm) is greater than the calculated value of MD3 (12,2 Nm), the selected cylinder is suitable for use.

See also other examples given for the S1 series and VL1 series rodless cylinders.