EP3322903A1 - Cylindre hydraulique à double effet - Google Patents

Cylindre hydraulique à double effet

Info

Publication number
EP3322903A1
EP3322903A1 EP16736882.8A EP16736882A EP3322903A1 EP 3322903 A1 EP3322903 A1 EP 3322903A1 EP 16736882 A EP16736882 A EP 16736882A EP 3322903 A1 EP3322903 A1 EP 3322903A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
double
pressure chamber
acting hydraulic
hydraulic cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16736882.8A
Other languages
German (de)
English (en)
Other versions
EP3322903B1 (fr
Inventor
Rolf Revenus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Maquet GmbH
Original Assignee
Maquet GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Maquet GmbH filed Critical Maquet GmbH
Publication of EP3322903A1 publication Critical patent/EP3322903A1/fr
Application granted granted Critical
Publication of EP3322903B1 publication Critical patent/EP3322903B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1438—Cylinder to end cap assemblies
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61G—TRANSPORT, PERSONAL CONVEYANCES, OR ACCOMMODATION SPECIALLY ADAPTED FOR PATIENTS OR DISABLED PERSONS; OPERATING TABLES OR CHAIRS; CHAIRS FOR DENTISTRY; FUNERAL DEVICES
    • A61G13/00—Operating tables; Auxiliary appliances therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a double-acting hydraulic cylinder with a first connection for acting on a first pressure chamber with a hydraulic fluid and a second connection for acting on a second pressure chamber with the hydraulic fluid.
  • FIG. 8 a shows an exemplary schematic diagram of a double-acting hydraulic cylinder 100 according to the prior art.
  • the known hydraulic cylinder 100 according to FIG. 8a comprises a cylinder housing 102 and a piston 104 guided in the cylinder housing 102.
  • the cylinder housing 102 comprises a first pressure chamber 106 formed by the cylinder housing 102 and a second pressure chamber 108 formed by the cylinder housing 102 the second pressure chamber 108 are separated from each other by the piston 104.
  • the first pressure chamber 106 is also referred to as cylinder chamber A, while the second pressure chamber 108 is also referred to as cylinder chamber B.
  • the cylinder chambers 106, A, and 108, B must be connected to a supply unit / control unit 110, which supply the hydraulic cylinder 100 with a liquid or gaseous medium.
  • the connection between the supply unit / control unit 110 and the connection 112 or 114 on the cylinder housing 102 is in each case via a flexible hose 116, 118.
  • a pressed-out ring eye 120 made of metal a Hohlsch raube 122 and two seals 124th 126, as shown schematically in FIG. 8c.
  • FIG. 8c shows in particular a schematic representation of an exposed hollow screw 122 of the known hydraulic cylinder 100 according to FIG. 8a.
  • a hose 116, 118 with a nominal diameter DN 3 and DN 4 is typically used in each case.
  • the screw has a height LI from the outer surface of the cylinder housing 102 to the end of the hollow screw 122 of about 15 mm.
  • the hoses 116, 118 are necessary when the cylinder 100 shown in Figure 8a is movably mounted.
  • FIG. 8b shows a schematic representation of a double-acting hydraulic cylinder 200 according to the prior art.
  • FIG. 8b shows, in particular, a spare part image of the double-acting hydraulic cylinder 200 of the series CSH1 MF3, MF4, MT4 and MS2 according to the Bosch Rexroth catalog with the catalog number RD17332 / 07.13.
  • it For double-acting hydraulic cylinders, it must be ensured at the A-side, ie the piston side, and be provided on the B-side, ie piston rod side, in each case a connection for a liquid medium. This is usually realized, as shown in FIG. 8 b, by a connection bore 212, 214 in the housing of the double-acting hydraulic cylinder 200.
  • the known, double-acting hydraulic cylinders have the disadvantage that, if the cylinder housing 102 shown in Figure 8a is used with the hose connections 112, 114 in tight spaces, the hollow screw 122 shown in Figure 8c is very exposed and disturbing at the respective end of the tube. This is particularly disadvantageous in that approximately 15 mm of space in the length or width of the hydraulic cylinder are lost. Furthermore, the known, double-acting hydraulic cylinders have the disadvantage that a shearing of the exposed hollow screw 122 at close components in the moving hydraulic cylinders due to the high cylinder forces during the movement is easily possible. In addition, the hose connections 116, 118 shown in Figure 8a are relatively susceptible to damage in the known double-acting hydraulic cylinders.
  • a double-acting hydraulic cylinder having the features of claim 1, a compact and robust construction of the double-acting hydraulic cylinder and at the same time a reliable operation of the same are achieved, since in particular a first cylinder housing, a piston guided in the first cylinder housing and a second cylinder housing are provided.
  • a first pressure chamber and a second pressure chamber are provided, which are separated from each other by the piston.
  • a first connection serves at least for supplying a hydraulic fluid to the first pressure chamber, while a second connection serves at least for supplying the hydraulic fluid to the second pressure chamber.
  • the second cylinder housing surrounds the first cylinder housing at least in one section.
  • the first connection and the second connection are arranged on a side facing away from the second pressure chamber end of the double-acting hydraulic cylinder.
  • the second pressure chamber can be acted upon by the hydraulic fluid via the section in which the second cylinder housing surrounds the first cylinder housing.
  • this port may be provided on the A side of the double-acting hydraulic cylinder.
  • the A side is on a first side of the piston while the B side is on a second side of the piston opposite the first side.
  • the double-acting hydraulic cylinder can be avoided. Furthermore, a shearing of an exposed connection element, such. As an exposed hollow screw can be avoided. In addition, the operation of the double-acting hydraulic cylinder can be prevented from causing damage to the connecting tubes extending between the ports of the double-acting hydraulic cylinder and the supply / control unit (such as a hydraulic power unit). This allows the compact and robust construction of the double-acting hydraulic cylinder and at the same time the reliable operation of the same.
  • the second cylinder housing surrounds the first cylinder housing at least in a portion along the longitudinal axis of the double-acting hydraulic cylinder.
  • a portion in which the second cylinder housing surrounds the first cylinder housing may be provided, this portion extending along the longitudinal axis of the double-acting hydraulic cylinder.
  • the first pressure chamber is a piston-side pressure chamber
  • the second pressure chamber is a piston rod-side pressure chamber
  • the hydraulic cylinder is in particular a differential cylinder.
  • a piston-side pressure space and a piston rod-side pressure space of a differential cylinder can be provided, which are each formed by the first cylinder housing.
  • the second pressure chamber facing away from the end of the double-acting hydraulic cylinder is limited by a cylinder bottom.
  • the cylinder bottom may enclose an end of the first cylinder housing facing away from the second pressure chamber and an end of the second cylinder housing facing away from the second pressure chamber.
  • the second pressure chamber facing away from the piston-side ends of the first and second cylinder housings can be firmly connected to the cylinder bottom.
  • a first sealing element is arranged between the second pressure chamber remote from the end of the first cylinder housing and the cylinder bottom. Furthermore, between the The second pressure chamber facing away from the second end of the second cylinder housing and the cylinder bottom arranged a second sealing element.
  • a first and second sealing element can be provided with the aid of which the second pressure chamber remote from the end of the first cylinder housing or the second pressure chamber opposite end of the second cylinder housing and the cylinder bottom can be sealed against each other.
  • first port and the second port are arranged on the cylinder bottom.
  • both the first port and the second port may be provided at an end remote from the second pressure chamber end of the double-acting hydraulic cylinder.
  • the first terminal comprises a first passage opening.
  • the first passage opening extends from a lateral surface of the cylinder bottom to the first pressure chamber.
  • a first passage opening can be provided, via which the first pressure chamber with the hydraulic fluid can be acted upon.
  • the second terminal comprises a second passage opening.
  • the second passage opening extends from a side surface of the cylinder bottom to the portion where the second cylinder housing surrounds the first cylinder housing.
  • a second passage opening can be provided, via which the second pressure chamber can be acted upon by the hydraulic fluid.
  • the first cylinder housing and the second cylinder housing are arranged such that a gap between the first cylinder housing and the second cylinder housing is formed.
  • the intermediate space extends from the end remote from the second pressure chamber of the double-acting hydraulic cylinder up to a first pressure chamber remote from the end of the double-acting hydraulic cylinder.
  • a gap between the first and second cylinder housing can be provided, this gap serves to establish a connection of the second pressure chamber with the second port at the end remote from the second pressure chamber end of the double-acting hydraulic cylinder.
  • the double-acting hydraulic cylinder comprises a rod bushing.
  • the rod bushing is disposed at an end of the first and second cylinder housings facing away from the first pressure chamber. Further, the rod bushing is formed such that a piston rod connected to the piston upon application of the hydraulic fluid to the first pressure chamber is moved in a first piston movement direction and upon application of the second pressure chamber with the hydraulic fluid in a second piston movement direction opposite to the first piston movement direction.
  • a rod bushing can be provided on the piston rod end of the double-acting hydraulic cylinder, which closes an end of the hydraulic cylinder facing away from the first pressure chamber.
  • the rod bushing comprises a recess.
  • the second pressure chamber via the portion in which the second cylinder housing surrounds the first cylinder housing, and acted upon via the recess of the rod bushing with the hydraulic fluid.
  • the piston rod-side pressure space can be easily and reliably supplied with the hydraulic fluid by means of the second port provided at the piston-side end of the double-acting hydraulic cylinder.
  • the first cylinder housing preferably comprises a first cylinder tube and the second cylinder housing comprises a second cylinder tube.
  • the double-acting hydraulic cylinder comprises at least a first holding element for holding the second cylinder housing.
  • the at least one first holding element is arranged at least in sections around the second cylinder housing on an outer surface of the second cylinder housing.
  • the first and second cylinder housings can be easily and securely held on the cylinder bottom by means of the at least one first retaining element.
  • the first connection is designed such that it can be connected to a first connection line at least for supplying the hydraulic fluid.
  • the second connection is designed such that it can be connected to a second connection line at least for supplying the hydraulic fluid.
  • two suitable ports can be provided for connection to a hydraulic power pack.
  • the double-acting hydraulic cylinder may in particular be a differential cylinder, constant-velocity cylinder or tandem cylinder.
  • Figure la is a schematic, perspective view of a double-acting
  • Hydraulic cylinder according to an embodiment
  • Figure lb is a schematic plan view of the double-acting hydraulic cylinder of Figure la;
  • Figure 2 is a schematic longitudinal sectional view along the section line
  • Figure 3 is a schematic longitudinal sectional view along the section line
  • Figure 4a is a schematic longitudinal sectional view along the section line
  • Figure 4b is a schematic representation of a piston end of the in
  • FIG. 5 shows an exemplary schematic diagram of a double-acting hydraulic cylinder according to an embodiment
  • FIG. 6 a shows a schematic illustration of a double-acting hydraulic cylinder with a first connection and a second connection according to an exemplary embodiment
  • Figure 6b is a schematic representation of a double-acting hydraulic cylinder with a connection on the B side of the double-acting hydraulic cylinder according to the prior art
  • Figure 7a is a schematic longitudinal sectional view of a double-acting
  • Hydraulic cylinder according to an embodiment
  • Figure 7b is a schematic longitudinal sectional view of a double-acting
  • FIG. 8a shows an exemplary schematic diagram of a double-acting hydraulic cylinder according to the prior art
  • Figure 8b is a schematic representation of a double-acting hydraulic cylinder according to the prior art.
  • Figure 8c is a schematic representation of an exposed hollow screw of the known, double-acting hydraulic cylinder of Figure 8a.
  • Figure la shows a schematic, perspective view of a double-acting hydraulic cylinder 10 according to an embodiment.
  • a double wall cylinder is shown in a cutaway view.
  • the double-acting hydraulic cylinder 10 comprises a first cylinder tube 14, a second cylinder tube 16 and a piston 26.
  • the piston 26 is connected to a piston rod 24.
  • the longitudinal axis 30 of the double-acting hydraulic cylinder 10 extends through a center of the piston rod 24 along a longitudinal extent of the piston rod 24.
  • the first and second cylinder tubes 14, 16 are arranged concentrically around this longitudinal axis 30 of the double-acting hydraulic cylinder 10 around.
  • the first cylinder tube 14 is provided, on which the piston 26 slides sealed and generates the force of the actuator. Furthermore, the second cylinder tube 16 is arranged around this first cylinder tube 14. A first piston rod side end of the second cylinder tube 16 is sealed to a rod bush 22. A first end opposite the second end of the cylinder tube 16 is sealed to a cylinder base 12.
  • the first cylinder tube 14 serves as an inner cylinder tube
  • the second cylinder tube 16 serves as an outer cylinder tube.
  • the second cylinder tube 16 is held on the cylinder bottom 12 via a wire ring 20a and an annular retaining element 20b by means of screws 46a to 46d.
  • the cylinder bottom 12 and the annular holding member 20b form a portion the double-acting hydraulic cylinder 10.
  • the second cylinder tube 16 is sealed against this section. In the sectional view of Figure la, the screw 46d is not shown.
  • the double-acting hydraulic cylinder 10 comprises a connection 34 for pressurizing a piston rod-side pressure chamber 38 with a hydraulic fluid.
  • this connection 34 is provided in the cylinder bottom 12.
  • the arranged in the cylinder bottom 12 port 34 is preferably connected via holes with the gap 40 between the first and second cylinder tube 14, 16.
  • the piston-rod-passage closure 22 arranged on the piston rod end of the double-acting hydraulic cylinder 10 comprises a groove 42.
  • This closure 22 may also be referred to as a rod bushing.
  • the hydraulic fluid is introduced into the piston rod side pressure chamber 38 via this groove 42 in the rod bush 22.
  • the double-acting hydraulic cylinder 10 shown in FIG. 1 a comprises a connection 32 for pressurizing the piston-side pressure chamber 36 with the hydraulic fluid and for discharging hydraulic fluid from this pressure chamber.
  • This connection 32 and the piston-side pressure chamber 36 are not shown in FIG. 1a.
  • For installation in a cylindrical bore of the formed by the second cylinder tube 16 shell diameter is the relevant size.
  • FIG. 1b shows a schematic plan view of the double-acting hydraulic cylinder 10 according to FIG.
  • the cylinder bottom 12 with the screws 46a to 46d extending through the cylinder bottom 12 is shown schematically.
  • Figure lb is used to illustrate a first to third section line 48a, AA, 48b, BB, and 48c, CC, with respect to the cylinder bottom 12.
  • Figures 2, 3 and 4a are sectional views of sections along the first shown in Figure lb to third section line 48a to 48c.
  • FIG. 2 shows a schematic sectional view of a longitudinal section along the section line 48a, AA in FIG. 1b.
  • the double-acting hydraulic cylinder 10 comprises the first cylinder tube 14 and the one guided in the first cylinder tube 14 Piston 26.
  • the first cylinder tube 14 preferably comprises the piston-side pressure chamber 36 formed by the first cylinder tube 14 between the piston 26 and the first end of the cylinder tube 14 closed by the cylinder base 12 and the piston rod-side pressure chamber 38 formed by the first cylinder tube 14 between the piston 26 and the closed by the rod bush 22 second end of the cylinder tube 14.
  • the piston-side pressure chamber 36 and the piston rod-side pressure chamber 38 are separated by the second piston 26 from each other.
  • the closed by means of the rod sleeve 22 second end of the first cylinder tube 14 is also referred to as a piston rod side end
  • closed by means of the cylinder bottom 12 second end of the cylinder tube 14 is also referred to as the piston side end.
  • a first sealing member 18a is disposed between the piston-side end of the first cylinder tube 14 and the cylinder bottom 12. Further, a second sealing member 18 b is disposed between the piston-side end of the second cylinder tube 16 and the cylinder bottom 12. In addition, a third seal member 18 c may be provided, which is disposed between the piston rod side end of the second cylinder tube 16 and the rod bush 22.
  • the first to third seal members 18a to 18c comprise a static seal member such as a seal member. B. an ing.
  • the second cylinder tube 16 can be securely sealed against the cylinder bottom 12 or the rod bush 22 at its piston-side and piston rod-side end.
  • the double-acting hydraulic cylinder 10 comprises a first and second screw connection 28a, 28b.
  • the first screw 28a is used to connect the piston 26 to the piston rod 24, while the second screw 28b is used to connect a piston rod side unit with the piston rod 24.
  • the first and second threaded connections 28a, 28b include a thread disposed on the piston rod side end of the piston rod 24.
  • the rod bushing 22 serves to linearly guide the piston rod 24 and the piston 26 connected to the piston rod 24. As shown schematically in FIG. 2, the piston rod 24 and the piston 26, respectively, are acted on the piston-side pressure chamber 36 with the hydraulic fluid in a first piston movement direction PI shifted linearly.
  • the piston rod 24 or the piston 26 is linearly displaced in a second piston movement direction P2.
  • the first and second piston movement directions PI, P2 substantially parallel to the longitudinal axis 30 of the double-acting hydraulic cylinder 10.
  • the first and second piston movement directions PI, P2 represent opposite piston movement directions of the double-acting hydraulic cylinder 10.
  • FIG. 2 shows that the second cylinder tube 16 surrounds the first cylinder tube 14 at least in a section 41.
  • this portion 41 extends along the longitudinal axis 30 of the double-acting hydraulic cylinder 10.
  • the gap 40 formed by the first and second cylinder tubes 14, 16 extends substantially within this portion 41.
  • the gap 40 extends substantially from the cylinder bottom
  • the groove 42 corresponds in particular to a recess of the rod bushing 22, which extends from the intermediate space 40 to the piston rod-side pressure chamber 38.
  • the dimension Dl shown in FIG. 2 is given by an outer surface 44 of the second cylinder tube 16. This dimension Dl corresponds to an installation space for the double-acting hydraulic cylinder 10.
  • FIG. 3 shows a schematic longitudinal section along the section line 48b, B-B in FIG. 1b.
  • the first connection 32 for applying pressure to the piston-side pressure chamber 36 is clearly visible.
  • the first port 32 comprises a first through-opening 33.
  • This first through-opening 33 preferably extends from a lateral surface 62 of the cylinder bottom 12 to the piston-side pressure chamber 36.
  • the first through-opening 33 extends essentially perpendicular to the first through-opening 33 side surface 62 of the cylinder bottom 12.
  • the first terminal 32 serves to connect a first connecting line 52. This first connecting line 52 is not shown in FIG.
  • FIG. 4a shows a schematic longitudinal sectional illustration along the section line 48c, CC in FIG. 1b.
  • the second connection 34 is clearly visible for acting on the piston rod-side pressure chamber 38.
  • the second connection 34 comprises a second through-opening 35.
  • This second through-opening 35 preferably extends from a lateral surface 62 of the cylinder bottom 12 to the intermediate space 40 formed by the first and second cylinder tubes 14, 16 the second passage opening 35 from the gap 40 obliquely upwards.
  • the second connection 34 serves to connect a second connection line 54.
  • This second connection line 54 is not shown in FIG. 4a.
  • the second connection 34, the intermediate raum 40, the recess 42 of the rod bushing 22 and the piston rod-side pressure chamber 38 connected to each other.
  • FIG. 4b shows a schematic illustration of a piston-side end of the double-acting hydraulic cylinder 10 shown in FIG. 1a.
  • the first and second ports 32, 34 are clearly visible in FIG. 4b.
  • the first port 32 extending through the cylinder bottom 12 is arranged, for example, in a middle region of the double-acting hydraulic cylinder 10
  • the second port 34 extending through the cylinder bottom 12 is arranged, for example, in a lateral region of the double-acting hydraulic cylinder 10
  • both the first port 32 and the second port 34 may be provided on the piston-side end of the double-acting hydraulic cylinder 10.
  • FIG. 5 shows an exemplary schematic diagram of a double-acting hydraulic cylinder 10 according to one exemplary embodiment.
  • the double-acting hydraulic cylinder 10 comprises only a single cylinder tube 14.
  • the double-acting hydraulic cylinder 10 according to the embodiment of Figure 5 does not include the second cylinder tube 16 of the double-acting hydraulic cylinder 10 according to the embodiment of Figure la.
  • the embodiment of Figure 5 relates to another aspect of the present invention.
  • the double-acting hydraulic cylinder 10 shown in FIG. 5 comprises the piston 26 guided in the cylinder tube 14, which separates the piston-side pressure chamber 36 from the piston rod-side pressure chamber 38.
  • the piston-side and piston rod-side pressure chamber 36, 38 are formed by the cylinder tube 14.
  • a piston rod side rod sleeve 22 is provided which receives the piston rod 24 and leads linearly.
  • the double-acting hydraulic cylinder 10 comprises the first and second ports 32, 34.
  • the first port 32 serves to pressurize the piston-side pressure chamber 36 with a hydraulic fluid
  • the second port 34 serves to pressurize the piston rod-side pressure chamber 38 with the hydraulic fluid is used.
  • the first connection 32 comprises a first passage opening 33
  • the second connection 34 comprises a second passage opening 35.
  • these first and second through openings 33, 35 extend completely through the piston rod 24.
  • the first and second through openings 33, 35 extend substantially parallel to the longitudinal axis 30 of the double-acting hydraulic cylinder 10.
  • the first extends Through opening 33 from a piston 26 facing away from the end of the piston rod 24 through the piston rod 24 through to a piston 26 facing the end of the piston rod 24.
  • the second through hole 35 from the piston 26 remote from the end of the piston rod 24 through as shown in Figure 5 the first through hole 33 further extends from the end of the piston rod 24 facing the piston 26 parallel to the longitudinal axis 30 of the double-acting hydraulic cylinder 10 and completely through the piston rod 24
  • the second passage opening 35 continues to angled away from the end of the piston rod 24 facing the piston 26 and partially through the piston 26 as far as the piston rod side pressure chamber 38 extends.
  • the piston-side and piston rod-side pressure chamber 36, 38 can be acted upon by the hydraulic fluid via the first or second port 32, 34 provided in the piston rod 24.
  • FIG. 6 a shows a schematic representation of a double-acting hydraulic cylinder 10 with a first connection 32 and a second connection 34 according to one exemplary embodiment.
  • the first and second ports 32, 34 are arranged on the cylinder bottom 12 of the double-acting hydraulic cylinder 10.
  • the first and second connections 32, 34 are connected to a hydraulic unit 50.
  • the first port 32 is connected via a first connecting line 52 to an A port of the hydraulic unit 50
  • the second port 34 is connected via a second connecting line 54 to a B port of the hydraulic unit 50.
  • the A port of the hydraulic unit 50 is used to supply the first port 32 with a hydraulic fluid
  • the B port of the hydraulic unit 50 is used to supply the second port 34 with the hydraulic fluid.
  • the piston rod side end of the double-acting hydraulic cylinder 10 is connected to a piston rod side unit 56.
  • the piston rod side unit 56 can be displaced by means of the double-acting hydraulic cylinder 10 in the first and second piston movement direction PI, P2.
  • the installation space 58 for the double-acting hydraulic cylinder 10 is shown in FIG. 6a.
  • the installation space 58 is in Figure 6a shown schematically by dashed lines.
  • the installation space 58 is essentially provided by the outer surface 44 of the second cylinder tube 16.
  • the installation space 58 essentially corresponds to the dimension D1 shown in FIG. 2.
  • the installation space 58 for the double-acting hydraulic cylinder 10 according to the exemplary embodiment of FIG. 6a is relatively small in comparison to the prior art.
  • FIG. 6 b shows a schematic representation of a double-acting hydraulic cylinder 100 with a connection 114 on the B side of the double-acting hydraulic cylinder 100.
  • the connection 114 arranged on the piston rod end of the double-acting hydraulic cylinder 100 is shown in FIG. 6 b.
  • the other port 112, which is located at the piston-side end of the double-acting hydraulic cylinder 100, is not shown in FIG. 6b.
  • These connections 112, 114 are connected via two connection lines 52, 54 to the A connection or B connection of a hydraulic unit 50.
  • the installation space 128 for the double-acting hydraulic cylinder 100 according to FIG. 6b is shown schematically by dashed lines.
  • the installation space 128 is given essentially by the lateral extent of the surface of the cylinder tube 102 and the exposed hollow screw 122.
  • the installation space shown in Figure 6b 128 according to the prior art is relatively large compared to the installation space 58 according to the embodiment of Figure 6a.
  • FIG. 7 a shows a schematic longitudinal sectional representation of a double-acting hydraulic cylinder 10 according to one exemplary embodiment.
  • the installation space 58 is shown in FIG. 7a.
  • the second connection 34 comprises an exposed hollow screw 60.
  • the exposed hollow screw 60 preferably extends through a ring eye 64 into the second through opening 35.
  • the exposed hollow screw 60 is on the cylinder bottom 12 arranged.
  • the exposed hollow screw 60 shown in FIG. 7 a serves to connect the second connecting line 54.
  • the dimensions D1 to D4 are shown in FIG. 7a.
  • the dimension Dl corresponds to the outer diameter of the second cylinder tube 16
  • the dimension D2 corresponds to the inner diameter of the first cylinder tube 14
  • the dimension D3 corresponds to the wall thickness of the first and second cylinder tubes 14, 16
  • the dimension D4 corresponds to the wall thickness of the first cylinder tube 14.
  • the dimension Dl are 50 mm
  • the dimension D2 is 35 mm
  • the dimension D3 is 7.5 mm
  • the dimension D4 is 3.5 mm.
  • Figure 7b shows a schematic longitudinal sectional view of a double-acting hydraulic cylinder 100 according to the prior art. In Figure 7b, the installation space 128 is clearly visible.
  • the dimensions LI to L3 are shown in Figure 7b.
  • the dimension L2 corresponds to the inner diameter of the cylinder tube 102, while the dimension L3 corresponds to the wall thickness of the cylinder tube 102.
  • the dimension LI is 20 mm, the dimension L2 35 mm and the dimension L3 3.5 mm.
  • FIG. 7a can be maintained at an operating pressure of 70 to 300 bar at a piston diameter or inner diameter D2 of the first cylinder tube 14 of 35 mm according to the present invention by skillful placement of the second port 34 of the outlined, cylindrical mounting space 58.
  • the determining outer diameter Dl of the lateral surface 44 is only 50 mm.
  • This outer diameter D1 of the lateral surface 44 is at most 7.5 mm larger than the piston diameter or inner diameter D2 of the first cylinder tube 14. With other piston diameters and comparable pressure, the dimension 7.5 remains constant.
  • the port 114 or the exposed hollow screw 122 typically protrudes 23.5 mm beyond the piston diameter or inner diameter L2 of the cylinder tube 102. Because of the drawn thread depth in a hollow screw M8xl typically used, the known solution can not be optimized as the inventive solution.
  • Embodiments of the present invention provide a space-saving, secure supply of energy within a double-acting hydraulic cylinder 10 and attaching the A and B ports 32, 34 on the cylinder housing 12 close to each other.
  • the installation space 58 can be made significantly smaller in diameter by the solution according to the invention. As a result, in particular space is saved.
  • the solution according to the invention relates above all to double-acting hydraulic cylinders.
  • the double-acting hydraulic cylinder 10 according to the present invention can be used in particular on operating tables. If the supply unit / control unit 50 of the cylinder 10 is preferably attached to the kinematics of the cylinder bottom 12 during long travel distances of the cylinder 10, the connecting lines 52, 54 do not experience any relative movement with respect to the two terminals 32, 34. If one were to attach the supply unit / control unit 50 to the rod-side unit 56, the hoses would be a large change in length experienced during extension of the cylinder 10.
  • the solution according to the invention makes it possible to also attach the B-connection 34 to the cylinder base 12. This is not possible in the prior art.
  • the connection 114 at the rod end over the ring eye 120 must be mounted unfavorably.
  • the exposed hollow screw 122 eliminates the threaded bushing 120 on the lateral surface of the cylinder tube 102.
  • a damage of the exposed hollow screw 122 by the movements of the cylinder 10 or mounting on the bore 128 can be excluded because the hollow screw 60 in the inventive solution to the cylinder bottom 12 is mounted outside of the installation space 58.
  • the supply of the B-side with the hydraulic fluid can be performed via the double tube solution according to the invention instead of via the externally laid lines according to the prior art.
  • the short flexible leads according to embodiments are much less susceptible to damage.
  • the supply of hydraulic fluid can also be realized via the piston rod 24, as shown in the embodiment of Figure 5.
  • two holes 33, 35 may be performed in the piston rod 24 or a plurality of tubes are pushed into each other to obtain two separate, oil-bearing spaces.
  • the A port 32 and the B port 34 are disposed at the outer end of the piston rod 24.
  • the embodiment shown in Figure 5 has the disadvantage over the embodiment shown in Figure la, that the cross section of the piston rod 24 through the oil holes 33, 35 is weakened.
  • resulting from the structure of Figure 5 compared to the structure of Figure la relatively high costs through the holes 33, 35th
  • the double-acting hydraulic cylinder can also be designed as a synchronizing cylinder or tandem cylinder. LIST OF REFERENCE NUMBERS

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Abstract

L'invention concerne un cylindre hydraulique à double effet (10) comprenant un premier carter de cylindre (14) et un piston (26) guidé dans le premier carter de cylindre (14), une première chambre de pression (36) et une deuxième chambre de pression (38) séparées l'une de l'autre par le piston (26) étant ménagées dans le premier carter de cylindre (14). Un premier raccordement (32) sert au moins à l'amenée d'un liquide hydraulique à la première chambre de pression (36), et un deuxième raccordement (34) sert au moins à l'amenée du liquide hydraulique à la deuxième chambre de pression (38). Par ailleurs, un deuxième carter de cylindre (16) entoure le premier carter de cylindre (14) au moins dans une partie (41). Le premier raccordement (32) et le deuxième raccordement (34) sont agencés au niveau d'une extrémité du cylindre hydraulique à double effet (10) opposée à la deuxième chambre de pression (38). La deuxième chambre de pression (38) peut être soumise à l'action du liquide hydraulique par l'intermédiaire de la partie (41), dans laquelle le deuxième carter de cylindre (16) entoure le premier carter de cylindre (14).
EP16736882.8A 2015-07-14 2016-07-11 Cylindre hydraulique à double effet Active EP3322903B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015111403.8A DE102015111403A1 (de) 2015-07-14 2015-07-14 Doppeltwirkender Hydraulikzylinder
PCT/EP2016/066438 WO2017009291A1 (fr) 2015-07-14 2016-07-11 Cylindre hydraulique à double effet

Publications (2)

Publication Number Publication Date
EP3322903A1 true EP3322903A1 (fr) 2018-05-23
EP3322903B1 EP3322903B1 (fr) 2022-03-02

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EP16736882.8A Active EP3322903B1 (fr) 2015-07-14 2016-07-11 Cylindre hydraulique à double effet

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US (1) US10514050B2 (fr)
EP (1) EP3322903B1 (fr)
JP (1) JP6945519B2 (fr)
KR (1) KR20180030591A (fr)
CN (1) CN107923421B (fr)
BR (1) BR112018000735A2 (fr)
DE (1) DE102015111403A1 (fr)
RU (1) RU2018105075A (fr)
WO (1) WO2017009291A1 (fr)

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DE102017105015B4 (de) 2017-03-09 2019-10-10 Tyrolon-Schulnig Gmbh Greif- und Transportvorrichtung
CA3073109A1 (fr) * 2017-08-16 2019-02-21 Kyntronics Llc Actionneur electrohydraulique
JP7446145B2 (ja) * 2020-04-07 2024-03-08 東京エレクトロン株式会社 基板処理装置
DE102021114066A1 (de) * 2021-05-31 2022-12-01 Jungheinrich Aktiengesellschaft Fahrwerkzylinder für ein Flurförderzeug mit einem gegenüber dem Boden vorgespannten Antriebsrad
DE102023200931A1 (de) * 2023-02-06 2024-08-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung eingetragener Verein Hydraulikzylinder, Verfahren zu seiner Herstellung und damit ausgestatteter Bohrhammer

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6280268B1 (en) * 1999-03-19 2001-08-28 Showa Corporation Tilt device for marine propulsion unit

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2832656A (en) * 1957-10-01 1958-04-29 Cecil F Perry Medical examining table
GB937765A (en) * 1960-07-22 1963-09-25 Armstrong Patents Co Ltd Improvements in or relating to hydraulic actuating mechanisms
DE2121042C3 (de) * 1971-04-29 1976-01-08 Weiss Kg Sondermaschinentechnik, 7141 Neckarweihingen Druckmittelbeaufschlagte Stellvorrichtung mit Eilgang und Krafthub
SE396801C (sv) * 1976-02-03 1986-06-09 Hiab Foco Ab Dubbelverkande hydraulcylinder med tva koncentriska mantlar
JPH0440013Y2 (fr) * 1986-06-18 1992-09-18
JPS63104704U (fr) * 1986-12-26 1988-07-07
CN87211000U (zh) * 1987-07-27 1988-05-25 康民权 闭式手动双作用液压缸装置
US5117741A (en) * 1990-01-16 1992-06-02 Sta-Rite Industries, Inc. Double wall hydraulic cylinder
DE29902773U1 (de) * 1999-02-17 1999-05-12 Bümach Engineering International B.V., Emmen Druckmittelbetriebener Arbeitszylinder mit fluidischer Wegsperrung
JP2000337313A (ja) * 1999-05-27 2000-12-05 Kinki Ishiko Kk 複動油圧シリンダ装置
FR2810701B1 (fr) * 2000-06-27 2002-12-13 Hydraulique Production Systems Verin hydraulique a double effet avec dispositif de blocage axial
CN2460766Y (zh) * 2000-12-16 2001-11-21 王日暖 等推力双级双作用液压缸
CN1526960A (zh) * 2003-09-25 2004-09-08 浙江大学 能平衡重量的单出杆等面积双作用液压缸
DE102005061730B4 (de) * 2005-11-18 2009-07-23 Tr Electronic Gmbh Vorrichtung zum Bewegen eines Kolbens
JP4353333B2 (ja) * 2007-03-30 2009-10-28 Ｓｍｃ株式会社 複動形エアシリンダの位置決め制御機構
CN201050516Y (zh) * 2007-06-04 2008-04-23 南通液压机械有限公司 多级同步伸缩双作用液压缸
DE102007048907A1 (de) * 2007-10-11 2009-04-16 Alpha Fluid Hydrauliksysteme Müller GmbH Zylinderbaugruppe
DE102014110670B4 (de) * 2014-06-23 2017-10-12 Notum Gmbh Betätigungs- und/oder Hubzylinder sowie Vorrichtung zum gesteuerten Bewegen eines Funktions- und/oder Maschinenelementes

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6280268B1 (en) * 1999-03-19 2001-08-28 Showa Corporation Tilt device for marine propulsion unit

Also Published As

Publication number Publication date
JP6945519B2 (ja) 2021-10-06
JP2018520322A (ja) 2018-07-26
CN107923421A (zh) 2018-04-17
EP3322903B1 (fr) 2022-03-02
DE102015111403A1 (de) 2017-01-19
KR20180030591A (ko) 2018-03-23
RU2018105075A (ru) 2019-08-14
CN107923421B (zh) 2019-12-20
US10514050B2 (en) 2019-12-24
WO2017009291A1 (fr) 2017-01-19
BR112018000735A2 (pt) 2018-09-04
US20180156247A1 (en) 2018-06-07

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