DE102015223000A1 - Hydraulic arrangement for a working machine and method for a hydraulic arrangement - Google Patents

Abstract

Disclosed is a hydraulic arrangement with a first hydraulic machine for a slewing gear of an excavator and a second hydraulic machine for a boom of the excavator. When braking the slewing and the lowering of the boom a flywheel for recovering the energy is driven by appropriate means. The arrangement is designed such that the stored energy in the flywheel for the boom and not for the slewing is used.

Description

The invention is based on a hydraulic arrangement with a flywheel for storing energy according to the preamble of claim 1. Furthermore, the invention proceeds from a method for energy recovery for such a hydraulic arrangement.

From the publication SU 1382920 A1 Such a hydraulic arrangement is known. Here, a flywheel for storing energy is provided.

In the publication RU 2 237 135 C1 Another embodiment of a hydraulic arrangement with a flywheel is disclosed. Here, a hydraulic motor is driven by consumers, which in turn drives a flywheel. With the flywheel, a hydraulic pump can be driven as a pressure medium source.

A disadvantage of the known solutions is that they are designed to be expensive in terms of device technology.

In contrast, the invention has for its object to provide a hydraulic arrangement which eliminates the disadvantages mentioned. Furthermore, the invention has for its object to provide a simple method for energy recovery for such a hydraulic arrangement.

The object with regard to the hydraulic arrangement is achieved according to the features of claim 1 and with regard to the method according to the features of claim 14.

Other advantageous developments of the invention are the subject of further subclaims.

According to the invention, a hydraulic arrangement for a work machine, in particular for an excavator, is provided. This has a first hydraulic consumer and at least one second hydraulic consumer. For storing recovered energy of at least the first consumer, in particular during deceleration of the first consumer, a flywheel or a flywheel is provided. The energy recovered and stored by the flywheel is advantageously used only for the at least one second consumer and not for the first consumer.

This solution has the advantage that the arrangement is designed such that the recovered energy is not used for the first and the second consumer, whereby a device-technical effort is reduced.

Preferably, the first consumer is a hydraulic machine for a slewing gear of the excavator. For example, energy can be easily recovered during fluidic braking of the slewing gear. The second consumer is preferably a hydraulic cylinder for a boom of the excavator, which allows the recovery of energy during lowering. The recovered energy is then advantageously reused to lift the boom. The energy required to lift the boom is usually greater than an energy input for turning the slewing, thus advantageously the energy recovered from the slewing gear is used for the boom and can not be reused for the slewing, which in addition, as already explained above, a device-technical Effort compared to the prior art is reduced.

In a further embodiment of the invention, a hydraulic machine is provided, which is mechanically connected to the flywheel, so that recovered energy can be supplied via the hydraulic machine to the flywheel and reused energy can be provided by the flywheel to drive the hydraulic machine. The hydraulic machine is thus preferably used as a hydraulic motor and as a hydraulic pump. In a further embodiment, the hydraulic machine is pivotable, whereby, for example, a brake pressure for the first and / or for the second consumer is adjustable. Further advantageously, the hydraulic machine is durchschwenkbar to set a flow rate and a swallowing amount proportional.

Advantageously, the first and the at least one second consumer are so operatively connected to the flywheel that the energy is simultaneously recoverable from the first consumer and the at least one second consumer. For example, for this purpose, the hydraulic machine can be driven by both consumers. The hydraulic machine is then connected to the first consumer in such a way that it can not convey any pressure medium back to it. The at least one second consumer can be driven by the hydromachine via the flywheel to reuse the energy.

So that pressure equalization can be effected by the consumers when the hydraulic machine is simultaneously being driven, a throttle valve is fluidically arranged between the first consumer and the hydraulic machine and, between the at least one second consumer and the hydraulic machine, a further throttle valve is arranged fluidically. With the respective throttle valve, a flow cross-section between the hydraulic machine and the respective consumer, in particular in the recovery of energy, be set proportionally. Thus, with respect to the first consumer with an arrangement of a throttle valve between this and the hydraulic machine recording the amount of energy that arises when braking a Oberwangens of the excavator from an open hydraulic circuit or slewing circuit via the throttle valve (throttle control) are passed to the hydraulic machine and by the Flywheel or be cached by a flywheel energy storage. Alternatively, it is conceivable to provide only one throttle valve in order to equalize the different pressure levels of the consumers.

In an alternative embodiment, the hydraulic machine can only be driven by the at least one second consumer to recover the energy, and this in turn can be driven by the hydraulic machine. In addition, a second hydraulic machine is connected to the flywheel, which is then drivable by the first consumer. Preferably, this can then not drive the first consumer, which means they can be configured simply as a hydraulic motor device technology. The recording of the amount of energy that arises during braking of the superstructure of the excavator can thus be done from the open turning circle by the second hydraulic machine, the flow rate is preferably adjustable in proportion to the speed of the superstructure. The arrangement of two hydraulic machines with a simultaneous recovery of energy from the slewing and from the boom or from the first consumer and the second consumer no throttling is necessary. Furthermore, for example, a recovery of energy from the slewing is enabled when the boom is lifted.

In a further embodiment of the invention, the pressure medium can be traceable on the output side of the second hydraulic machine to a low pressure side of the first consumer. For this purpose, check valves may be provided. For example, both pressure sides of the first consumption are each connected to an outlet side of the second hydraulic machine via a non-return valve which opens in the direction of the consumer.

Device-technically simple, the second hydraulic machine, as already stated above, can only be used as a hydraulic motor. Furthermore, the second hydraulic machine can simply be a constant machine in terms of device technology. Alternatively, it is conceivable that this is designed to be pivotable.

Advantageously, the hydraulic cylinder is a differential cylinder whose pressure chambers are connectable via a connecting valve. Thus, in the recovery of the energy in the hydraulic cylinder, a pressure level can be adjusted. With the connecting valve, for example, a flow cross section of a pressure medium flow path between the pressure chambers is continuously adjustable. The hydraulic cylinder preferably has a piston which separates a cylinder space from an annular space penetrated by a piston rod. When lowering the boom, the piston is preferably moved in the direction of a reduction of the cylinder space, the connecting valve can then be opened so that pressure fluid can flow from the cylinder chamber to the annulus, which carries only one surface on the piston, which is equivalent to the cross-sectional area of the piston rod, and thus increases the pressure in the cylinder chamber. The pressure medium connection between the pressure chambers can be adjusted in dependence on the pressure in the cylinder chamber, in turn, to set a pressure in the annulus, without providing a pressure sensor for the annulus.

Preferably, a pressure sensor for measuring pressure is arranged on the side of the cylinder space of the hydraulic cylinder. Depending on the measured value determined by the pressure sensor and in dependence on a deflection of an actuating element (joystick), a lowering speed of the hydraulic cylinder can be determined (throttle control). Furthermore, in this case the hydraulic machine connected to the flywheel can be adjusted accordingly.

Advantageously, at least one supply unit in the form of a hydraulic machine is provided for supplying the pressure medium to the consumer. The supply unit is preferably controlled in such a way that, when the energy is returned to the second consumer, a power output of the at least one supply unit is preferably dependent on the recirculated energy and can preferably be reduced approximately at the level of the recirculated energy. The supply unit can be driven, for example, via an electric drive or an internal combustion engine. Preferably, a further second supply unit is provided in the form of a hydraulic machine, which can be driven together with the first supply unit in terms of device technology, for example via a common drive shaft. Furthermore, the supply units are device technology simply not durchschwenkbar. It is conceivable that the first supply unit is provided for the second consumer and the second supply unit for the first consumer. In a further embodiment of the invention, the supply unit or the supply units are hydraulic pumps which are proportionally adjustable.

A flow cross-section between a supply unit or both supply units and the second consumer, in particular during the supply of the second consumer with recirculated energy, can be reducible, for example by a throttle element or by a plurality of throttle elements. Thus, not only the supply unit or the supply units can be reduced in terms of their power output when recycling the energy from the flywheel, but it can also be a flow cross section can be reduced.

Preferably, the hydromachine used to return the energy is associated with a swivel angle sensor and / or a rotational speed sensor to determine an actual flow rate of the hydraulic machine. Furthermore, a speed sensor or for both supply units, a common speed sensor or a respective speed sensor can be provided for the supply unit. In addition, a swivel angle sensor or a swivel angle sensor for both supply units can be provided for the supply unit. Thus, the current flow rate of the supply unit or the supply units can be determined.

In a further embodiment of the invention means may be provided to use a volume flow of a pressure medium of the first and / or second consumer in the recovery of energy to a part for driving the flywheel and the other part to a tank, in particular via a valve to dismiss , Thus, when storing the available energy from the individual consumers, the volume flow of the pressure medium can be divided depending on the system state, so that the pressure medium can be conveyed to the tank both to the hydraulic machine and, in particular via a control block.

Preferably, the flywheel is mechanically coupled via a transmission with the hydraulic machine or with both hydraulic machines, whereby a certain speed ratio is possible. If two hydraulic machines are provided for energy recovery, the second hydraulic machine is preferably connected to the first hydraulic machine via a through drive, with which the hydraulic machines can be mechanically connected in series with the flywheel. Alternatively, the hydraulic machines can also be mechanically connected in parallel, for example via a transfer case with the flywheel.

Advantageously, a valve block between the second hydraulic machine and the first consumer is arranged, whereby at a release / activation of a higher pressure side can be connected to the second hydraulic machine.

In a method according to the invention for energy recovery in a hydraulic arrangement according to one of the preceding aspects, pressure medium is preferably substantially unthrottled during deceleration, wherein corresponding throttle valves are opened, promoted by one or both consumers to the hydraulic machine used as a hydraulic motor. Alternatively or additionally, when the pressure medium is fed back, it can flow substantially unrestrictedly from the hydraulic machine used as a hydraulic pump into the hydraulic cylinder of the boom, in that the corresponding valve or the corresponding valves are open. A speed of the boom can then be determined by the speed and / or by the tilt angle of the hydraulic machine.

When lowering the boom, the connecting valve for the pressure chambers of the hydraulic cylinder can be fully or partially opened as needed.

A required speed of the individual consumers can be determined without direct position or speed measurement on the basis of the driver requirement, that is to say from a variable of a deflection of a corresponding actuating element.

Several embodiments of an inventive arrangement are shown in the drawings. With reference to the figures of these drawings, the invention will now be explained in more detail.

Show it

1 a hydraulic circuit diagram of a first embodiment,

2 a hydraulic circuit diagram of a second embodiment,

3a and 3b each a hydraulic circuit diagram of a third and a fourth embodiment,

4 a hydraulic circuit diagram of a fifth embodiment and

5 schematically the arrangement according to a sixth embodiment.

1 shows a hydraulic arrangement 1 for an excavator. This has a first consumer 2 in the form of a hydraulic machine for a slewing gear of the excavator and a second consumer 4 , the two hydraulic cylinders for a boom of the Excavator has. For energy recovery are both consumers 2 . 4 fluidly with a hydraulic machine 6 connected via a gearbox 8th mechanically with a flywheel 10 is coupled. About the hydraulic machine 6 One is the flywheel 10 drivable and on the other hand, the flywheel 10 the hydraulic machine 6 power to recover recovered energy for the second consumer 4 to use again. For pressure medium supply of the consumer 2 and 4 are two supply units 12 and 14 provided, which are designed as pivotable hydraulic pumps. These are via a common drive shaft of a drive unit 16 drivable. In addition to the consumers 2 and 4 are two more consumers 18 and 20 each provided in the form of a hydraulic cylinder. The consumers 2 . 4 . 18 and 20 are over a valve block 21 with the supply units 12 . 14 connected.

The first consumer 2 is preferably used in an open hydraulic circuit. The hydraulic machine 22 of the consumer 2 has a first print page 24 and a second pressure side 26 , These are above the valve block 21 alternately either with one of the supply units 12 . 14 or both supply units 12 . 14 or a tank 28 connectable. Via a first pressure relief valve 30 is the first printed page 24 with the second pressure side 26 connectable. About another second pressure relief valve 32 is then the second print page 26 with the first print page 24 connectable. For speed measurement of the hydraulic machine 22 is a speed sensor 34 provided with the direction of rotation is detected. In addition, with the valve block 21 the first print page 24 over to the pressure side 24 opening check valve 36 and the second print page 26 with one going to the print side 26 opening check valve 38 connected. When braking the first consumer 2 and thus the slewing pressure medium from the first pressure side via a first check valve 40 or from the second print side 26 via a second check valve 42 tapped. A respective check valve 40 and 42 opens here in the pressure fluid flow direction to the hydraulic machine 6 , Downstream of the check valves 40 and 42 is a common throttle valve 44 provided with a flow cross-section in the flow path between the check valves 40 and 42 and the hydraulic machine 6 is continuously adjustable.

The throttle valve 44 has an input port E to which the check valves 40 and 42 are connected and an output terminal A, the input side with the hydraulic machine 6 connected is. An input-side pressure of the throttle valve 44 is from a pressure sensor 46 measured. A valve spool of the throttle valve 44 is acted upon in the direction of closed positions via a spring force of a valve spring and opposite in the direction of opening positions of an actuator with an actuating force. The actuator is powered by an Electronic Control Unit (ECU) 48 driven.

The second consumer 4 has a first hydraulic cylinder 50 and a second hydraulic cylinder 52 , These are arranged fluidically parallel to each other. A respective hydraulic cylinder 50 . 52 , has a piston 54 on, each one cylinder space 56 from one of a piston rod 58 interspersed annulus 60 separate. The cylinder chambers 56 are with the annuli 60 via a connecting valve 62 connectable. This is according to the throttle valve 44 designed and has an input terminal E, with the cylinder chambers 56 is connected, and an output terminal A, which is connected to the annular spaces 60 connected is. The connection valve 62 is at a pressure medium flow path 64 between the cylinder chambers 56 and the hydraulic machine 6 over to the connection valve 62 opening check valve 66 connected. About the connection valve 62 especially when lowering the boom and thus at a reduction of the cylinder spaces 56 this throttled with the annuli 60 or, if necessary, also be connected unthrottled, with a throttling pressure in the cylinder chambers 56 increases. Thus, the connection valve 62 preferably always open when lowering the boom. A pressure in the cylinder chambers 56 is via a pressure sensor 68 measurable. Furthermore, the cylinder chambers 56 over a connecting line 73 and the annuli 60 over a connecting line 75 with the valve block 21 connected.

In the pressure medium flow path 64 is a throttle valve 70 arranged according to the throttle valve 44 is designed. This has an input port E, with the cylinder chambers 56 is connected and an output terminal A, which is connected to the hydraulic machine 6 connected is. Between the throttle valve 70 and the cylinder chambers 56 branches the connecting valve 62 from. Both the connection valve 62 as well as the throttle valve 70 are also via the ECU 48 controllable. A pressure on the output side of the throttle valve 70 is via a pressure sensor 72 detectable. The output sides A of the throttle valve 44 and 70 are connected to each other and to a working port X of the hydraulic machine 6 connected.

The hydraulic machine 6 has next to the working port X a tank connection T, with the tank 28 connected is. The hydraulic machine 6 can be used as a hydraulic pump and hydraulic motor. It can be swiveled, whereby a delivery volume in pump operation and a displacement in engine operation are adjustable. The working connection X of the hydraulic machine 6 is further to the tank 28 about one check valve 77 connected in the fluid flow direction away from the tank 28 opens.

The adjustment of the supply units 12 . 14 and the hydraulic machine 6 via the ECU 48 , The valve block 21 is also via the ECU 48 controllable. Furthermore, the sensors 46 . 68 and 72 with the ECU 48 connected. In addition, there is a speed sensor 74 for the hydraulic machine 6 and a speed sensor 76 for the supply units 12 . 14 intended. In addition, the hydraulic machine 6 and the supply units 12 . 14 each a swivel angle sensor 78 . 80 , respectively 82 assigned. The sensors 74 to 82 are also with the ECU 48 connected. To control the consumer 2 . 4 . 18 and 20 are actuators 84 in the form of joysticks provided with the ECU 48 are connected.

When braking the slewing gear, so the first consumer 2 , the throttle valve 44 open. The hydraulic machine 6 is then driven as a hydraulic motor. The swivel angle of the hydraulic machine 6 is adjusted such that the entire volume flow from the first consumer 2 and possibly also from the boom, so the second consumer 4 , can be recorded. A braking force is determined by a back pressure. The hydraulic machine 6 then again drives over the gearbox 8th the flywheel 10 at. Thus, when lowering the boom pressure fluid from the second consumer 4 to the hydraulic machine 6 can flow is the throttle valve 70 also open here. An opening cross-section of the throttle valves 44 and 70 is chosen so that the pressure levels of consumers 2 and 4 on the output side of the throttle valves 44 and 70 be aligned. The pressure sensor 68 together with a deflection of at least one of the actuators 84 (Throttle control) indicates how fast the boom of the second consumer 4 should be lowered. Accordingly, the hydraulic machine 6 set.

For feeding back pressure medium into the cylinder chambers 56 of the consumer 4 promotes the hydraulic machine 6 as a hydraulic pump via the open valve 70 Pressure fluid from the tank 28 , An extension speed of the boom is determined by the speed and the swivel angle of the hydraulic machine 6 when the valve 70 is fully open.

According to 2 is different from 1 In addition, a hydraulic machine in the form of a hydraulic motor 86 intended. The throttle valve 44 is then no longer on the output side with the hydraulic machine 6 but with the hydraulic motor 86 via a connecting cable 88 connected. The adjustable in its displacement hydraulic motor 86 has an input terminal E, which is connected to the connecting line 88 and an output terminal A connected to an output line 90 connected is. The output line 90 opens between the check valves 36 and 38 to pressure medium for low-pressure side pressure 24 respectively 26 feed. The hydraulic motor 86 is about a through drive 92 to the hydraulic machine 6 connected. Furthermore, the connection cable 88 via a check valve 93 to the tank 28 connected, with the check valve in the flow direction away from the tank 28 opens.

The hydraulic motor 86 is now drivable especially when braking the slewing gear. The hydraulic machine 6 In contrast, it is driven by the boom and can extend it. By the arrangement of the hydraulic motor 86 can with simultaneous recovery of energy from the slewing and from the boom this without throttling by the throttle valves 44 . 74 respectively. It is conceivable that the throttle valve 44 and / or the throttle valve 70 is saved / become.

According to 3a is different from 2 for the recovery of energy of the first consumer a hydraulic motor 94 provided, which is designed as a constant motor. Furthermore, between the hydraulic motor 94 and the throttle valve 44 a pressure sensor 96 intended.

The pressure relief valves 30 and 32 are on the output side between the check valves 36 and 38 over a connecting line 98 connected. Furthermore, a feed pump 100 provided, the pressure fluid from the tank 28 in the output line 90 can promote. On the output side of the feed pump 100 this is via a check valve 102 with the tank 28 connected, wherein the check valve in the pressure fluid flow direction away from the tank 28 closes.

According to 3b is different from 3a the hydraulic motor 94 by a swiveling hydraulic motor 104 replaced.

In 4 are the hydraulic machine 6 and the hydraulic motor 104 arranged mechanically parallel. This is the gearbox 8th designed accordingly. In contrast, in the embodiments of the 2 to 3b the machines for energy recovery are arranged mechanically in series.

According to 5 is schematically the flywheel 10 shown that over the gearbox 8th with the hydraulic machine 6 and the hydraulic motor 94 respectively 104 connected is. Between the first consumer 2 and the hydraulic machine 94 respectively 104 is a first valve block 106 arranged and between the second consumer 4 and the hydraulic machine 6 is a second valve block 108 arranged.

Disclosed is a hydraulic arrangement with a first hydraulic machine for a slewing gear of an excavator and a second hydraulic machine for a boom of the excavator. When braking the slewing and the lowering of the boom a flywheel for recovering the energy is driven by appropriate means. The arrangement is designed such that the stored energy in the flywheel for the boom and not for the slewing is used.

LIST OF REFERENCE NUMBERS

1

 arrangement

2

 first consumer

4

 second consumer

6

 hydromachine

8th

 transmission

10

 flywheel

12

 supply unit

14

 supply unit

16

 drive unit

18

 consumer

20

 consumer

21

 manifold

22

 hydromachine

24

 first print page

26

 second print side

28

 tank

30

 Pressure relief valve

32

 Pressure relief valve

34

 Speed sensor

36

 check valve

38

 check valve

40

 check valve

42

 check valve

44

 throttle valve

46

 pressure sensor

48

 Electronic Control Unit

50

 first hydraulic cylinder

52

 second hydraulic cylinder

54

 piston

56

 cylinder space

58

 piston rod

60

 annulus

62

 connecting valve

64

 Pressure fluid flow path

66

 check valve

68

 pressure sensor

70

 throttle valve

72

 pressure sensor

73

 connecting line

74

 Speed sensor

75

 connecting line

76

 Speed sensor

77

 check valve

78

 Swing angle sensor

80

 Swing angle sensor

82

 Swing angle sensor

84

 actuators

86

 hydraulic motor

88

 connecting cable

90

 output line

92

 drive-through

93

 check valve

94

 hydraulic motor

96

 pressure sensor

98

 connecting line

100

 feed pump

102

 check valve

104

 hydraulic motor

106

 first valve block

108

 second valve block

e

 input port

A

 output port

X

 working port

T

 tank connection

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• SU 1382920 A1 [0002]
• RU 2237135 C1 [0003]

Claims (14)

Hydraulic arrangement for a working machine with a first hydraulic consumer ( 2 ) and a second hydraulic consumer ( 4 ), whereby one flywheel ( 10 ) is provided, with the recovered energy of at least the first consumer ( 2 ) is storable, characterized in that the arrangement is designed such that the recovered energy for the at least one second consumer ( 4 ) and not for the first consumer ( 2 ) can be used. Arrangement according to claim 1, wherein the first consumer ( 2 ) a hydraulic machine ( 22 ) is for a slewing gear of an excavator. Arrangement according to claim 2, wherein the energy of the slewing gear during braking is recoverable. Arrangement according to one of claims 1 to 3, wherein the second consumer ( 4 ) a hydraulic cylinder ( 50 ) is for a boom of the excavator. Arrangement according to claim 4, wherein the recovered energy is used for lifting the boom. Arrangement according to one of the preceding claims, wherein a hydraulic machine ( 6 ) with the flywheel ( 10 ), which is used as a hydraulic motor and as a hydraulic pump and is used for the recovery and reuse of energy. Arrangement according to claim 6, wherein the hydraulic machine ( 6 ) is pivotable. Arrangement according to one of the preceding claims, wherein the first consumer ( 2 ) and the second consumer ( 4 ) in such a way with the flywheel ( 10 ) are in operative connection, that the energy from the first consumer ( 2 ) and the second consumer ( 4 ) is recoverable. Arrangement according to one of claims 6 to 8, wherein the hydraulic machine ( 6 ), in particular exclusively by the second consumer ( 4 ) is drivable and this of the hydraulic machine ( 6 ), and wherein a second hydraulic machine ( 86 ) with the flywheel ( 10 ), in particular exclusively from the first consumer ( 2 ), or where both consumers ( 2 . 4 ) fluidly with the hydraulic machine ( 6 ) Are connected and this is driven by them. Arrangement according to claim 9, wherein seen fluidically between the first consumer ( 2 ) and the hydraulic machine ( 6 ) a throttle valve ( 44 ) is arranged and / or fluidly seen between the second consumer ( 4 ) and the hydraulic machine ( 6 ) is arranged a throttle valve, or being fluidly seen between the first consumer ( 2 ) and the second hydraulic machine ( 86 ) a throttle valve ( 44 ) is arranged and / or fluidly seen between the second consumer ( 4 ) and the hydraulic machine ( 6 ) a throttle valve ( 70 ) is arranged. Arrangement according to one of claims 4 to 10, wherein the hydraulic cylinder ( 50 ) a differential cylinder with a piston ( 54 ), which is a cylinder space ( 56 ) of an annulus ( 60 ), the rooms being connected via a connecting valve ( 62 ) are connectable. Arrangement according to one of the preceding claims, wherein the pressure medium supply to the consumer ( 2 . 4 ) at least one supply unit in the form of a hydraulic machine ( 12 ), wherein when the energy is returned to the second consumer ( 4 ) a power output of the at least one supply unit ( 12 ) is reduced as a function of the recirculated energy. Arrangement according to claim 10 or 11, wherein the flywheel ( 10 ) of the slewing gear ( 2 ) and from the boom ( 4 ) for energy recovery via the common hydraulic machine ( 6 ) or in each case via a hydraulic machine ( 6 . 86 ) is drivable, the slewing ( 2 ) and the boom ( 4 ) in each case via the proportionally adjustable throttle valve ( 44 . 70 ) with the common hydraulic machine ( 6 ) or their respective hydraulic machine ( 6 . 86 ) and wherein the hydromachine connected to the boom ( 6 ) is pivotable and can be used as a hydraulic motor and as a hydraulic pump, and wherein the at least one supply unit is a hydraulic pump ( 12 ), which is the main source of pressure for the slewing gear ( 2 ) and the boom ( 4 ) is provided and via a valve block ( 21 ) and / or via valves with the slewing gear ( 2 ) and the boom ( 4 ), the arrangement being such that the recovered energy for driving the cantilever ( 4 ) and not for driving the slewing gear ( 2 ) is reused. Method for energy recovery in a hydraulic arrangement according to one of the preceding claims, wherein during braking of the slewing gear ( 2 ) and / or lowering the boom ( 4 ) Pressure means substantially unthrottled by one or both consumers ( 2 . 4 ) for use as a hydraulic motor ( 6 Hydraulic machine used, and / or wherein at a reuse of energy pressure fluid substantially unthrottled from the hydraulic machine used as a hydraulic pump ( 6 ) in the hydraulic cylinder ( 50 ) of the jib ( 4 ) flows, with a speed of the boom ( 4 ) by a rotational speed and / or a swivel angle of the hydraulic machine ( 6 ) is determinable.

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