DE102019004338A1 - HYDRAULLIC CYLINDER DRIVE AND HYDRAULLIC PRESS DRIVE AND HYDRAULIC DRIVE PROCESS - Google Patents

Abstract

The invention relates to a hydraulic cylinder drive (1) comprising at least one cylinder-piston device (2) arranged on at least one cylinder with a cylinder-piston (3), a cylinder-piston chamber (4) and, preferably, a cylinder-annular chamber ( 5), a cylinder pump arrangement (7) fluidly connected to the cylinder piston device (2) with at least one cylinder pump (8, 9), and the cylinder annulus (5) and / or the cylinder piston chamber ( 4) with a pressure medium (6) fluidly supplying pressure lines (D1, D2, D3). The cylinder-piston device (2) comprises a reversible cylinder, in particular a differential cylinder. The cylinder pump arrangement (7) can be driven in terms of speed and / or direction of rotation. The at least one cylinder pump (8, 9) is designed as a variable displacement pump with a variable cylinder pump swivel angle.

Description

FIELD OF THE INVENTION

The invention relates to a hydraulic cylinder drive according to the preamble of claim 1. For example for die cushion applications or for forming applications in general, for example for forming processes with counter-forces, for displacement devices or for processes clamped by a cylinder ensemble, or for die cushions for drawing presses Sheet metal forming, for counterholders in gear presses with a counterpressure principle, for counterholders in cold extrusion presses with a counterpressure principle, or for counterpressure cylinders in pipe bend presses, such cylinders are used or used. The cylinders described here are regularly used in machine forming, in particular in deep drawing, or in other machine pressing processes. With the help of hydraulically or pneumatically operated die cushions, forming processes are influenced locally, for example to avoid wrinkles.

The cylinder drive described here for the various pressing and / or forming processes comprises at least one cylinder-piston device arranged on at least one cylinder with a cylinder-piston and a cylinder-piston chamber. The piston device can have features of a plunger pump or a plunger. A cylinder annulus can, preferably, be provided. The cylinder-piston delimits the piston space and the annular space and is movable therein. The cylinder drive further comprises a cylinder pump arrangement with at least one cylinder pump that is fluidly connected to the cylinder piston device. In addition, the cylinder drive comprises pressure lines which fluidly supply the cylinder annulus and the cylinder piston space with a pressure medium.

The invention further relates to an accumulator-free hydraulic drive arrangement for driving a pressing device comprising an (additional) cylinder for forming devices according to the preamble of claim 9 and according to the preamble of claim 10. The pressing device comprises a press-piston device which is connected via a press Pump arrangement and hydraulically driven via connected pressure lines. The press-piston device has at least one press pump, comprising a pump shaft, which can preferably be driven in terms of speed and / or direction of rotation. The press-piston device also has a press pump drive which drives the at least one press pump. The at least one press pump is designed as a variable displacement pump with a variable press-pump swivel angle, and it can be swiveled, in particular by means of a press actuating device (external to the pump).

Finally, the invention relates to hydraulic drive methods according to the preamble of claim 16 and according to the preamble of claims 17 and 18.

TECHNOLOGICAL BACKGROUND

For example, in die cushion applications, a plunger displaces the die cushion, with the displacement forces reaching about 30% of the pressing force. The displacement forces also serve to "brake" the sheet's advancing movement during deep drawing. The force of the die cushion is generated hydraulically in most cases. Depending on the apparatus specifications regarding the controllability and / or the uniformity of the drawing or forming process, pneumatically operated cushion devices can alternatively be found.

In other forming applications, a ram or a cylinder component is also subjected to pressure / force and moved against a workpiece or by means of a tool against the form to be formed.

The counterforce exerted by this cylinder during operation of the cylinder drive depends on the requirements of the tool. A force that is essentially constant over the entire stroke is often sufficient. Most of the time, however, the drive is subjected to a force profile that varies over the stroke. The requirements for the exact observance of the force-displacement curve are often comparatively high, which usually justifies the use of dynamically regulating pressure valves within the drive arrangement.

When the pressurized cylinder is displaced by the device, oil in the piston chamber is expanded via a pressure valve and discharged into a tank. This results in a high power loss, which on the one hand affects the energy balance of the device and on the other hand leads to undesired oil heating, which in turn would have to be eliminated by complex and costly cooling measures.

In view of these disadvantages, hydraulic drive concepts have sometimes been designed, whereby the "dissipated" energy is to be recuperated at least in part. It was also considered to use a pump drive (motor) as a generator during the drawing or forming process, so that the electrical energy generated should at least partially be returned to the device.

The not inconsiderable expenditure on equipment is problematic, as are the losses observed in the case of multiple energy conversion (hydraulic to electrical - electrical to hydraulic - etc.). This is where the invention comes in.

PRESENTATION OF THE INVENTION

The object of the invention is to provide a hydraulic concept which is more efficient with regard to the operating and forming energy expenditure, in particular with reduced (power) losses. This object is achieved by a hydraulic cylinder drive according to claim 1. The cylinder drive is suitable for driving a cylinder component as a component of a forming device or a forming tool in general, for example a die cushion device, a counter pressure device, a pipe bending device or the like. In the case of the cylinder drive, a cylinder-piston device is provided which comprises a reversibly operating (differential) cylinder and in which the cylinder-pump arrangement can be driven in terms of speed and / or direction of rotation. The at least one cylinder pump is designed as a variable displacement pump with a variable cylinder pump swivel angle.

The pump or pumps can be designed, for example, as a pivotable axial piston pump, with operating parameters such as pressure, delivery volume and / or pump output depending, among other things, on the pivoting angle of the variable displacement pump. In the case of a die cushion device, the die cushion downward movement forcibly follows the ram. As a rule, the cushion also follows the subsequent upward movement of the ram, the pulled component is ejected. By providing a reversible (differential) cylinder, the cylinder can also be operated independently in both directions, for example when setting up the tool. The double-acting differential cylinder also offers the advantage of accelerating the cylinder before it hits the plunger in order to dampen the impact.

The cylinder pump arrangement preferably comprises two cylinder pumps with a variable swivel angle, which are connected to a (common) variable-speed cylinder pump drive (drive motor), for example via a common drive shaft. Motor speed and optionally also direction are controlled via a controller and / or a converter. It can be provided that the converter takes on controller functions.

The delivery volume of the two cylinder pumps is essentially a function of the area ratio of the differential cylinder contained in the cylinder drive. The direction of movement of the cylinder piston is generated by changing the direction of rotation of the cylinder pump drive, when installing an external control device and a pump that can be swiveled from -100% to + 100% delivery volume, alternatively also by swiveling in the other “sign area” (quadrants). The pivoting of the variable pump is controlled by algorithms that are processed in a control unit, for example within the converter.

Ultimately, the engine torque is used to regulate the cylinder force of the cylinder drive, which a converter that is inexpensive in terms of equipment and safety is able to fulfill, as a result of which the expenditure on equipment in connection with control aspects is reduced. An elaborate control unit, which is possibly prone to failure, can be dispensed with.

By providing one pump or preferably two pumps with a variable swivel angle, the delivery volume per engine revolution can be changed, depending on the pressure present. In this way, the maximum torque of the connected motor can be reduced, because at high pressure the cylinder speed is reduced in the same way as is usual with the press ram anyway. This means that a smaller, cheaper and ultimately more energy-efficient motor can be used.

A further gain in efficiency is achieved by using two pumps to adjust the flow rates for the ring and piston side of the differential cylinder. Any switching valves, check valves or accumulators described in the prior art can be dispensed with, which simplifies the apparatus, makes it less susceptible to faults and reduces acquisition and operating costs. The need for valves and accumulators also makes the cylinder drive safer. The hydraulic side of the cylinder control consists of almost fail-safe elements such as pumps and pressure lines. With the safety functions integrated in the converter and certified accordingly (e.g. "safe stop", "safe direction of movement", "safely reduced speed"), a cylinder drive can be implemented in an efficient and cost-effective manner that meets the legal safety requirements without any additional equipment , For example, set-up movements of the device at a safely reduced speed are possible without any significant additional outlay in terms of apparatus.

Another advantage is that the cylinder drive works autonomously without a direct connection to the drive technology of other devices, apparatus and / or devices. So it's one Can be used for hydraulic presses or for electromechanically driven presses. The electrical energy obtained in the cylinder drive can be recovered in both hydraulic and electromechanical systems for driving a press ram.

As a result, a cylinder drive concept that is improved compared to the prior art is realized, on the one hand with the described recuperation feature while avoiding double energy conversion, and on the other hand as a “low-cost” concept for comparatively simple applications.

According to a preferred embodiment of the cylinder drive, the cylinder pump arrangement can comprise a cylinder pump drive, for example an electric motor, for driving the cylinder pump. A cylinder gear arrangement can be provided, in particular for adapting the speeds, preferably the maximum speeds, of the cylinder pump drive and the cylinder pump, the cylinder gear arrangement being arranged between the at least one cylinder pump and the cylinder pump drive.

A converter can be used to control cylinder pump drive parameters, the parameters in particular comprising: direction of rotation and / or speed and / or torque of the cylinder pump drive (motor) and / or swivel angle of the cylinder variable displacement pump.

The cylinder pump swivel angle of the variable pump can be adjusted internally in the pump, in particular by means of pressure and / or torque of the cylinder pump drive. Alternatively, the cylinder-pump pivoting angle of the variable pump can be adjusted by means of at least one, in particular pump-specific and / or electromechanically drivable, actuating device, which can preferably be operated hydraulically or electromechanically. At least one (preferably one) converter can be provided to control this actuating device (s). At least one control valve can be provided, in particular in the case of a hydraulically adjustable pump.

In a variant of the cylinder drive concept, at least one pressure control valve can be provided, which is arranged in particular in a pressure line connecting the piston space or the annular space with a pressure medium tank. In particular, if the dynamics of the regulation of the engine speed and / or the pump swiveling device are not sufficient to represent the required course of the force-displacement course of the cylinder, a pressure control valve can be expedient.

A hydraulic concept, which is more efficient with regard to the operating or forming energy expenditure, in particular with reduced (power) losses, is further realized by an accumulator-free hydraulic drive arrangement for driving a pressing device comprising a cylinder for forming devices. In this drive arrangement, the cylinder for forming devices can be driven by means of a cylinder drive described here. In the case of presses with several cylinders for forming devices, each cylinder can optionally be equipped with its own pump unit and thus operated individually.

A, in particular independent, hydraulic concept, which is also more efficient with regard to the operating or forming energy expenditure, in particular with reduced (power) losses, is furthermore achieved by a pressure-free hydraulic drive arrangement for driving a pressing device comprising a cylinder for forming devices 10 realized. The pump shaft is a common shaft of the press pump (s) and the cylinder pump (s).

It may be expedient if a press gear arrangement is provided, in particular for adapting the speeds, preferably the maximum speeds, of the press pump drive and press pump (s), the press gear arrangement between the at least one press pump or the presses -Pumps and the press pump drive is arranged.

The press-piston device can comprise a rapid-motion piston. An auxiliary pump arrangement can also be provided, which is fluidly connected to the cylinder-piston chamber and / or to the cylinder-ring chamber and / or to a chamber, for example a piston or ring chamber of the rapid-motion piston, of the press-piston device.

According to a preferred variant, it is provided that the press pump arrangement comprises a first press pump and a second press pump. Individual or each of the press pumps can be designed as a double or multiple pump (s), in particular with their own actuating devices. The first press pump is fluidly connected to the press piston chamber of the press piston device. The second press pump is fluidly connected to the press annulus of the press piston device. The first press pump, the second press pump and the cylinder pump have a common pump shaft. A first press pump swivel angle of the first press pump is accordingly adjusted by means of at least one, in particular pump-external, first press actuating device, which can preferably be operated hydraulically or electromechanically. A second press pump swivel angle of the second press pump is adjusted by means of at least one, in particular pump-external, second press actuating device, which can preferably be operated hydraulically or electromechanically. The cylinder pump swivel angle of the cylinder pump is adjusted by means of at least one, in particular pump-external, cylinder actuating device, which can preferably be operated hydraulically or electromechanically. A converter arrangement can preferably be provided, which comprises a first converter for controlling the first press actuating device, a second converter for controlling the second press actuating device and a third converter for controlling the cylinder actuating device.

The recuperation can take place directly from the "braking" cylinder pump via the common shaft into the main piston pump. This avoids double conversion losses (hydraulics - electrics and electrics - hydraulics). Experience has shown that this leads to approximately 10% higher feedback values. At a cylinder output of approximately 20 kW, approximately 2 kW would be fed back, i.e. H. about 2 kW more than would be expected according to the prior art. This brings about a considerable increase in the efficiency of the device.

It is particularly advantageous that the regenerated cylinder energy accelerates the movement of the main tappet. If, for example, a drive motor with a maximum torque of approximately 200 Nm is in use, the piston pump of the press ram could essentially be used for a torque of approximately 60 Nm fed back via the cylinder 200 Nm + 60 Nm = 260 Nm because the recuperated energy is fed directly via the shaft. The ram speed increases by about 30%. When detouring via electrical recuperation, on the other hand, even with a torque of about 60 Nm fed back via the cylinder for the forming device, only 200 Nm would still be available on the motor shaft. The system would not be faster with purely electrical energy recovery, it would only draw less energy from the power grid.

When using a motorized swivel angle adjustment with servo motors, ball screw and correspondingly safe angle encoder on the motor, the safety functions integrated in the converter (e.g. "safe stop", "safe direction of movement", "safely reduced speed") can be used in a simple manner Drive can be realized that meets the legal safety requirements without additional equipment. This means that setup movements are also possible at a safely reduced speed. The additional brake on the motor means that even the highest safety requirements can be met (e.g. PLe according to EN 13849-1).

In addition to deep-drawing presses, the press drive concept described here can also be used for many other hydraulic machines with several, preferably counteracting, cylinders, for example for tube bending systems.

A particularly independent hydraulic concept, which is more efficient with regard to the operating or forming energy expenditure, in particular with reduced (power) losses, is also realized by a hydraulic drive method for driving a cylinder according to claims 16, 17 and 18. It can be provided that the recuperated energy output is supplied to the cylinder and / or the press used.

The size, shape, material selection and technical conception of the above-mentioned components as well as the components to be used according to the invention described in the exemplary embodiments are not subject to any special exceptional conditions, so that the selection criteria known in the field of application can be used without restriction.

Further details, features and advantages of the subject matter of the invention result from the subclaims, as well as from the following description and the associated drawing, in which an exemplary embodiment of a hydraulic drive concept for cylinders or for presses is shown. Individual features of the claims or the embodiments can also be combined with other features of other claims and embodiments.

list of figures

• 1A/B Varianten eines Zylinderantriebs, jeweils in schematischer Darstellung,
• 2 ein Antrieb einer Presseinrichtung mit Zylinder in schematischer Darstellung und
• 3A/B Varianten eines Pressenantriebs, bei dem Pressen-Pumpen und Zylinderpumpe auf einer gemeinsamen Pumpenwelle angeordnet sind, in schematischer Darstellung.

Show in the drawing

• 1A / B variants of a cylinder drive, each in a schematic representation,
• 2 a drive of a pressing device with cylinder in a schematic representation and
• 3A / B Variants of a press drive, in which press pumps and cylinder pumps are arranged on a common pump shaft, in a schematic representation.

DETAILED DESCRIPTION OF EMBODIMENTS

A schematic of a cylinder drive 1 can he 1 A be removed. This in 1A not shown) Tool (die cushion) is over a cylinder-piston device 2 in the form of a differential cylinder with force or pressure. The cylinder-piston device 2 includes a cylinder piston 3 which has a cylinder piston chamber 4 and a cylinder annulus 5 the piston device 2 limited. On the cylinder-piston chamber 4 is the pressure line D1 connected to the cylinder annulus the pressure line D2 , In the pressure lines D1 . D2 becomes a leverage 6 fluidly promoted.

The hydraulic cylinder drive 1 further includes a cylinder pump assembly 7 , The cylinder pump assembly 7 in turn includes a first, adjustable, cylinder pump 8th and a second, adjustable, cylinder pump 9 both through a common pump shaft 10 are mechanically coupled together. The pumps 8th . 9 can be formed, for example, as axial piston pumps. On the common pump shaft 10 is the electromotive cylinder pump drive 11 mechanically attached. The motor drive of the pumps 8th . 9 is variable in speed and / or variable in direction of rotation. The drive motor 11 is electrical with an inverter 12 connected. Between electric motor 11 and the pumps 8th . 9 is a cylinder gear 13 provided to adjust the respective speeds.

The on the cylinder piston chamber 4 arranged pressure line D1 is with the print side 14 the first cylinder pump 8th fluidly connected. The on the cylinder annulus 5 arranged pressure line D2 is with the print side 14 the second cylinder pump 9 fluidly connected.

According to 1A is a controller 15 provided the electrically with the converter 12 is connected (dashed line). With the controller 15 can, provided that this should be provided in the cylinder drive variant, other components of the drive device 1 be regulated / controlled. According to 1A they are a position sensor 16 to record the piston position and / or a pressure control valve 17 , The (optional) pressure control valve 17 can be useful if the dynamics of the control of the (hydraulic and / or mechanical) drive components are not sufficient to the required force-displacement curve of the cylinder 3 to realize. The pressure control valve 17 is in the pressure line D3 arranged which otherwise the pressure line D1 and a pressure medium tank 18 fluidly connects.

By the pumps 8th . 9 of the cylinder drive 1 according to 1A (internal to the pump) can be pivoted, for example depending on pressure or engine torque. B. the delivery volume per engine revolution changeable. In this way, the maximum torque of the connected motor 11 be reduced, because at high pressure the cylinder speed is reduced in the same way as is usual with the press ram anyway. This makes a smaller, less expensive motor 11 used. Finally, the use of two pumps allowed 8th . 9 according to 1A an efficient adjustment of the flow rates for the ring and piston side of the differential cylinder 2 ,

At the in 1B schematically illustrated variant of the cylinder drive 1 is an external control device 19 for swiveling the variable pumps 8th . 9 provided, each on a (separate) converter 20 an inverter arrangement 21 (electrically) connected. The converter arrangement 21 is electrical with the controller 15 connected. According to the 1B is a pressure control valve ( 17 ) not provided.

A hydraulic drive device without accumulator 100 for driving a pressing device comprising a cylinder for forming devices 150 is schematically in 2 displayed. The press facility 150 comprises a press-piston device also formed as a differential cylinder 102 , on which - according to one variant - a rapid traverse piston 151 is arranged. The press piston chamber 104 of the press differential cylinder 102 is with the print side 114 a first pump 108 a press-pump arrangement 107 via the pressure line L2 fluidly connected. The press annulus 105 of the press differential cylinder 102 is over the pressure line L1 fluidic with the pressure side 114 a second press pump 109 the press pump arrangement 107 connected. The suction side 122 the first press pump 108 is fluid with the piston chamber 152 of the rapid traverse piston 151 the press-piston device 102 via the pressure line L3 connected. The press pump assembly 107 includes a pump shaft 110 what common shaft of the first press pump 108 and the second press pump 109 is. One, preferably both, press pumps can be designed as a variable displacement pump, ie as pivotable pumps which can be pivoted by a pivoting angle in order to change the delivery volume per revolution.

The common pump shaft 110 the press pump arrangement 107 is mechanical with the press pump drive 111 connected, the press pump drive 111 as a variable-speed and / or variable-direction electric motor 111 is formed. Between the engine 111 and the pumps 108 . 109 is optionally a gear 113 arranged.

The press facility 150 according to 2 includes a cylinder drive 1 , its components and fluidic and electrical wiring - with the exception of an optional pressure control valve - already based on the 1A was explained. cylinder drive 1 and press pump assembly 107 or press-piston device 102 have a common pressure center tank 18 ,

The press drive variants according to the 3A and 3B include pump assemblies 107 with a first and a second press pump 108 . 109 as well as with a cylinder pump 8th , these three pumps (first press pump 108 , second press pump 109 and cylinder pump 8th ) on a common pump shaft 110 are mechanically connected. According to 3A is the print side 14 the pump 8th fluidly via the pressure line L5 with the piston chamber 5 the cylinder-piston device 2 connected and the suction side 22 the pump 8th over the line L4 with the cylinder annulus 4 , Each of the three pumps 8th . 108 . 109 is external to the pump using one actuator each 19 . 119 can be pivoted electromechanically or hydraulically. For every actuator 19 . 119 is an inverter for electromechanical adjustment 20 . 120 an inverter arrangement 121 provided that with hydraulic adjustment this would be a corresponding control valve. A fourth converter 120 is electric with the electromotive press pump drive 111 connected.

The arrangement of three variable pumps coupled on the shaft side 8th . 108 . 109 according to the in 3A shown drive concept enables an efficient energy-related exchange of power between the consumers to be driven ( 2 . 102 . 150 ). In this way, energy / performance can be recuperated and the installed components can be dimensioned smaller, which reduces manufacturing and operating costs.

According to the in 3B The variant of the drive concept shown is an auxiliary motor 153 and an associated auxiliary pump 154 provided, for example for the delivery of pressure medium in and / or from less performance-relevant volumes, such as the rapid traverse piston chamber 152 or the cylinder annulus 5 , The concept according to 3B allowed the pressure line L4 between the suction side 22 the cylinder pump 8th and the cylinder annulus 5 eliminated. The supply of the cylinder annulus 5 and the rapid traverse piston chamber 152 takes place via the auxiliary pressure line L6 and L7 , the print side 14 the auxiliary pump 154 over lines L6 and L7 with the annulus 4 is connected and with the piston chamber 152 of the rapid traverse piston 151 , The print page 14 the pump 8th is over the line L5 with the piston chamber 5 the cylinder-piston device 2 fluidly connected.

LIST OF REFERENCE NUMBERS

1

cylinder drive

2

Cylinder-piston means

3

Cylinder piston

4

Cylinder piston chamber

5

Cylinder annulus

6

lever

7

Cylinder pump assembly

8th

pump

9

pump

10

pump shaft

11

Cylinder pump drive, motor

12

inverter

13

Cylinder gear

14

pressure side

15

controller

16

position sensor

17

Pressure control valve

18

Pressure tank

19

setting device

20

inverter

21

Inverter arrangement

22

suction

100

driving means

102

Pressing-piston device

103

Pressing piston

104

Press piston chamber

105

Presses annulus

107

Press pump assembly

108

pump

109

pump

110

pump shaft

111

Press pump drive, motor

112

inverter

113

Presses transmission

114

pressure side

115

controller

116

position sensor

119

setting device

120

inverter

121

Inverter arrangement

122

suction

150

presser

151

Eilgangkolben

152

Eilgangkolbenraum

153

auxiliary engine

154

auxiliary pump

D1

pressure line

D2

pressure line

D3

pressure line

L1

pressure line

L2

pressure line

L3

pressure line

L4

pressure line

L5

pressure line

L6

pressure line

L7

pressure line

Claims (18)

Hydraulic cylinder drive (1) comprising at least one cylinder-piston device (2) arranged on at least one cylinder with a cylinder-piston (3), a cylinder-piston chamber (4) and, preferably, a cylinder-annular chamber (5), one Cylinder-pump arrangement (7) fluidly connected to the cylinder-piston device (2) with at least one cylinder pump (8, 9), and the cylinder annulus (5) and / or the cylinder-piston chamber (4) with one Pressure medium (6) fluid-supplying pressure lines (D1, D2, D3), characterized in that the cylinder-piston device (2) comprises a reversibly operating cylinder, in particular differential cylinder, that the cylinder-pump arrangement (7) speed and / or can be driven in a direction of rotation, and that the at least one cylinder pump (8, 9) is designed as a variable displacement pump with a variable cylinder pump pivoting angle. Cylinder drive (1) after Claim 1 , characterized in that the cylinder pump arrangement (7) comprises a cylinder pump drive (11) for driving the cylinder pump (8, 9). Cylinder drive (1) after Claim 2 , characterized by a cylinder gear arrangement (13), in particular for adapting the speeds, preferably the maximum speeds, of cylinder pump drive (11) and cylinder pump (8, 9), the cylinder gear arrangement (13) between the at least one Cylinder pump (8, 9) and the cylinder pump drive (11) is arranged. Cylinder drive (1) according to one of the Claims 1 to 3 , characterized by a converter (12) for controlling cylinder pump drive parameters, in particular comprising the direction of rotation and / or speed and / or torque of the cylinder pump drive (11) and / or swivel angle of the cylinder pump (8, 9). Cylinder drive (1) according to one of the Claims 1 to 4 , characterized in that an adjustment of the cylinder pump swivel angle of the variable pump (8, 9) takes place inside the pump, in particular by means of pressure and / or torque of the cylinder pump drive (11). Cylinder drive (1) according to one of the Claims 1 to 4 , characterized in that the cylinder-pump swivel angle of the variable pump (8, 9) is adjusted by means of at least one, in particular pump-external, cylinder actuating device (19), which can preferably be operated hydraulically or electromechanically. Cylinder drive (1) after Claim 6 , characterized by at least one converter (20) for controlling the at least one, in particular electromechanically drivable, cylinder actuating device (19), and / or by at least one control valve. Cylinder drive (1) according to one of the Claims 1 to 7 , characterized by at least one pressure control valve (17) which is arranged in particular in a pressure line (D3) connecting the cylinder piston chamber (4) or the cylinder ring chamber (5) with a pressure medium tank (18). Hydraulic drive arrangement (100) without an accumulator for driving a press device (150) comprising a cylinder for forming devices, the press device (150) comprising a press-piston device (102), which is connected via a press-pump arrangement (107) and via pressure lines connected to it (L1, L2, L3, L4, L5, L6, L7, D1, D2, D3) can be driven hydraulically, the press-piston device (101) using at least one press pump (1) comprising a pump shaft (110). 108, 109) which can be driven variable in speed and / or direction of rotation, the press piston device (102) having a press pump drive (111) which drives the at least one press pump (108, 109), and wherein the at least one press pump (108, 109) is designed as a variable displacement pump with a variable press-pump swivel angle, in particular by means of, preferably pump-external, press actuating device (119), characterized in that the cylinder for forming devices by means of a cylinder drive (1 ) according to one of the Claims 1 to 8th is drivable. Hydraulic drive arrangement (100) without an accumulator for driving a pressing device (150) comprising a cylinder for forming devices according to the preamble of Claim 9 , especially after Claim 9 , characterized in that the pump shaft (110) is a common shaft of the press pump (108, 109) and the cylinder pump (8). Drive arrangement (100) after Claim 9 or 10 characterized by a press gear arrangement (113), in particular for adapting the speeds, preferably the maximum speeds, of press pump drive (111) and press pump (108, 109), the press gear arrangement (113) between the at least one press -Pump (108, 109) and the press pump drive (111) is arranged. Drive arrangement (100) according to one of the Claims 8 to 11 , characterized in that the press-piston device (102) comprises a rapid-motion piston (151). Drive arrangement (100) according to one of the Claims 9 to 12 , characterized by an auxiliary pump arrangement (153, 154) which is fluidly connected to the cylinder-piston chamber (4) and / or to the cylinder-ring chamber (5) and / or to a chamber (152) of the press-piston Setup (102). Drive arrangement (100) according to one of the Claims 9 to 13 , characterized in that the press pump arrangement (107) comprises a first press pump (108) and a second press pump (109), the first press pump (108) being fluid with the press piston chamber (104) of the Press piston device (102) is connected, wherein the second press (109) pump is fluidly connected to the press annulus (105) of the press piston device (102), wherein the first press pump (108) , the second press pump (109) and the cylinder pump (8) have a common pump shaft (110), an adjustment of a first press pump swivel angle of the first press pump (108) by means of at least one, in particular pump-external, the first press actuating device (119), which can preferably be operated hydraulically or electromechanically, an adjustment of a second press pump pivoting angle of the second press pump (109) using at least one, in particular pump-external, second press actuating device (119) takes place, which can preferably be operated hydraulically or electromechanically, and wherein the cylinder-pump pivoting angle of the cylinder pump (8) is adjusted by means of at least one, in particular pump-external, cylinder actuating device (19), which is preferably operated hydraulically or electromechanically. Drive arrangement (100) after Claim 14 , characterized by a converter arrangement (121) comprising a first converter (120) for controlling the first press actuating device (119), a second converter (120) for controlling the second press actuating device (119) and a third converter (20 ) to control the cylinder actuator (19). Hydraulic drive method for driving a cylinder, characterized in that part of the drive energy with a cylinder drive according to one of the Claims 1 to 8th is recuperated. Hydraulic drive method for driving a pressing device comprising a cylinder, characterized in that part of the drive energy with a cylinder drive according to one of the Claims 1 to 8th recuperated and made available to the pressing device. Hydraulic drive method for driving a pressing device comprising a cylinder, in particular according to Claim 17 , characterized in that part of the drive energy with a drive arrangement according to one of the Claims 10 to 15 recuperated and made available to the pressing device.

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