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
  • F15B15/1423—Component parts; Constructional details
  • F15B15/1457—Piston rods
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C15/00—Disintegrating by milling members in the form of rollers or balls co-operating with rings or discs
  • B02C15/04—Mills with pressed pendularly-mounted rollers, e.g. spring pressed
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
  • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
  • B02C4/00—Crushing or disintegrating by roller mills
  • B02C4/28—Details
• • 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

Definitions

• the invention relates to a power transmission system having a hydraulic cylinder, which has a piston acted upon by hydraulic fluid and a pressure bearing in operative contact with the piston bearing having at least a first and a second sliding surface for exerting a sliding movement.
• Such a power transmission system is used for example in roller mills with at least one grinding roller and a rotatable grinding plate and a power arm, wherein the power arm is pivotally and rotatably supported in a bearing and the grinding roller is rotatably supported at the other end of the power arm.
• roller mill is known, for example, from JP-A-2000312832.
• the power transmission system serves to exert a force on the
• the power arm which then presses the grinding roller on the grinding table.
• the power arm executes a pivoting movement, so that it is in the range of
• the invention is therefore based on the object to provide a power transmission system, which is characterized by significantly reduced shear forces.
• the power transmission system essentially consists of a hydraulic cylinder which has a piston which can be acted upon by hydraulic fluid and a pressure bearing in operative contact with the piston, which has at least one first and one second sliding surface for the purpose of sliding movement.
• the thrust bearing also provides a pressure chamber, which communicates via at least one bore formed in the piston with the hydraulic fluid acted upon side of the piston. Due to the pressure chamber, there is a significant relief in the area of the sliding surfaces and also the transverse forces acting on the piston are reduced. Depending on the dimensions of the pressure chamber, reductions in the transverse forces in the range of 80 to 95% and more could be achieved.
• the thrust bearing is connected via a coupling rod with the hydraulic cylinder, wherein the coupling rod is articulated to allow the sliding movement of the thrust bearing.
• the coupling rod preferably extends through the bore of the piston and is mounted on the side facing away from the thrust bearing end face of the piston.
• a third and fourth sliding surface may also be provided for the purpose of pivoting movement.
• the first and second sliding surface of the thrust bearing can be aligned, for example, flat or transversely to the direction of movement of the piston, while the third or fourth sliding surface of the thrust bearing is spherical or spherical and the other sliding surface is designed as a complementary Jacobfikiee.
• a thrust bearing with four sliding surfaces preferably has the following components: a. a first pressure element whose one side is in operative connection with the piston and whose other side forms the first sliding surface, b. a second pressure element, one side of which forms the fourth sliding surface and the other side serves to transmit power and c. an intermediate element whose one side forms the second sliding surface and acts as a counter surface to the first sliding surface and whose other side forms the third sliding surface and acts as a counter surface to the fourth sliding surface.
• seals are provided between respectively associated sliding surfaces, ie between the first and second and the third and fourth sliding surface, the pressure building up in the pressure chamber relieves the associated sliding surfaces and the piston. It is therefore desirable to choose the resulting by the seals pressure surfaces in the pressure chamber preferably between 80 and 95% of the piston area. As a result, the acting transverse forces in the area of the sliding surfaces and of the piston are reduced by this percentage. It is of course also conceivable that the pressure surfaces are formed larger than the piston surface. But this has the consequence that the thrust bearing lifts and floats, so that the piston rod would have to be biased in a corresponding manner.
• the significant reduction of the transverse forces also has the advantage that the unit of hydraulic cylinder and thrust bearing can be built much more compact. A reduction of the size by 30% is not excluded. This also leads to a significant reduction in the cost of the thrust bearing.
• Fig. 2 is a partial sectional view of the power transmission system in the region of the thrust bearing
• Fig. 3 is a sectional detail view of a roller mill
• Fig. 4 is a sectional plan view of a roller press.
• the power transmission system illustrated in FIGS. 1 and 2 consists essentially of a hydraulic cylinder 1 which has a piston 10 which can be acted upon by hydraulic fluid and a thrust bearing 2 in operative contact with the piston.
• the thrust bearing essentially has the following components: a. a first pressure element 20, which is fastened with its one side to the lower end face of the piston 10 and whose other side forms a first sliding surface 20a, b. a second pressure element 21, one side of which serves as a fourth sliding surface 21a and the other side 21b for power transmission, and c. an intermediate element 22, one side of which forms the second sliding surface 22a, which acts as a counter surface to the first sliding surface 20a and whose other side forms a third sliding surface 22b, which acts as a counter surface to the fourth sliding surface 21a.
• a first seal 23 is provided between the first and second sliding surfaces 20a, 22a, and a second seal 24 is provided between the third and fourth sliding surfaces 22b, 21a.
• a pressure chamber 25 is thereby formed, which by the first and second pressure element 20, 21, the intermediate element 22 and a part of the thrust bearing facing end of the
• Piston 10 is limited.
• the pressure chamber 25 is connected via one or more holes 11 formed in the piston with the hydraulic fluid acted upon side of the piston 10 in
• a coupling rod 3 is further provided, which connects the thrust bearing 2 with the hydraulic cylinder 1, wherein the coupling rod is articulated both in the region of the thrust bearing and in the region of the piston to the
• the first and second sliding surfaces 20a, 22a are oriented transversely to the direction of movement of the piston and form a plane Gleitfikiee.
• a sliding surface is spherical or spherical and the other sliding surface is formed as a correspondingly complementary counter surface.
• the third and fourth sliding surface thus allow a pivoting movement of the thrust bearing.
• the pivot radius of the thrust bearing is turned off on the pivoting movement of the associated with the power transmission system power arm.
• the pressure surfaces defined by the seals 23, 24 should be as much as 80 to 95% of the cross-sectional area of the piston 10. The lateral forces are then reduced to a corresponding extent, so that the sliding surfaces are acted upon only with 5 to 20% of the pressure. A certain pressure in the area of the sliding surfaces seems appropriate, so that the
• Thrust bearing does not lift off and floats. Also the escape of hydraulic fluid can then be avoided more easily.
• the pressure surfaces formed by the seals 23, 24 could be up to 100 percent or more of the piston cross-sectional area. In the experiments on which the invention is based, however, it has been shown that a value of the pressure surfaces formed by the seals 23, 24 in the range from 75 to 99%, preferably between 80 and 95%, are ideal for highly dynamic applications.
• the residual pressure with which the sliding surfaces are printed together is advantageously transmitted via guide or support rings 26, 27, which are characterized by a particularly low coefficient of friction.
• the support ring 26 is therefore disposed between the first and second sliding surfaces 20 a, 22 a outside the seal 23.
• the support ring 27 is located outside the seal 24 between the third and fourth sliding surface 22b and 21a.
• the pressure bearing 2 described above has four sliding surfaces, it is of course also conceivable that only two sliding surfaces, for example, the first and second or the third and fourth sliding surface are provided.
• the thrust bearing is further surrounded by an outer wall 8 which is formed so flexible that it does not hinder the movement of the thrust bearing.
• This outer wall may also have a leakage port to return leaking hydraulic fluid to the reservoir.
• the roller mill shown schematically in Fig. 3 consists essentially of a grinding roller 4 and a rotatable grinding plate 5. Furthermore, a power arm 6 is provided which is supported pivotably and rotationally fixed in a bearing 7 designed as a fixed bearing, wherein the grinding roller 4 at the opposite end of Power arm is rotatably mounted. Further, a Power transmission system according to the above description, which acts with its hydraulic cylinder 1 and its thrust bearing 2 in a central region of the power arm 6 on this.
• the hydraulic cylinder 1 In order to adjust the pressure exerted by the grinding roller 4 on the grinding table 5 pressure, the hydraulic cylinder 1 is acted upon by a corresponding hydraulic pressure. The pivotal movement of the power arm 6 is compensated by the thrust bearing 2, so that the hydraulic cylinder 1 can be arranged fixed.
• a plunger cylinder is particularly suitable for the hydraulic cylinder.
• the power transmission system acts in a central region between the grinding roller 4 and bearing 7 on the power arm 6.
• the positions of bearing and power transmission system are reversed.
• FIG. 4 Another application example is illustrated in Figure 4 and illustrates a roller press with two counter-rotating grinding rollers 40, 50.
• the grinding roller 50 is mounted with a Mahlrollenachse 51 in a fixed bearing 52, while the grinding roller 40 is supported with its Mahlrollenachse 41 in a movable bearing 42 is.
• the grinding stock 70 to be comminuted is fed to the gap formed between the grinding rollers 40, 50 and comminuted between the rollers.
• a power transmission system according to the above description is provided, which is supported with its hydraulic cylinder 1 on a power frame 60 and is in operative contact with its thrust bearing 2 with the movable bearing 42.
• the Mahlrollenachsen are mounted in two bearings, so that s are also provided two power transmission systems.
• the power transmission system in a roller press is thus also suitable for compensating for an inclination of the two grinding rollers during operation.
• Hydraulic cylinders and thrust bearings can therefore be designed for the reduced lateral forces, resulting in a more compact design and can reduce the cost of manufacturing.

Landscapes

• Engineering & Computer Science (AREA)
• Food Science & Technology (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Crushing And Grinding (AREA)
• Support Of The Bearing (AREA)
• Vehicle Body Suspensions (AREA)
• Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
• Actuator (AREA)
• Friction Gearing (AREA)

Priority Applications (7)

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

Country Status (8)

Cited By (4)

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Citations (4)

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• 2008
  • 2008-02-22 DE DE102008010652A patent/DE102008010652B3/de active Active
• 2009
  • 2009-02-19 DK DK09707109.6T patent/DK2111510T3/da active
  • 2009-02-19 JP JP2010547179A patent/JP5313269B2/ja not_active Expired - Fee Related
  • 2009-02-19 CN CN200980105028.9A patent/CN101946097B/zh active Active
  • 2009-02-19 DE DE502009000572T patent/DE502009000572D1/de active Active
  • 2009-02-19 EP EP09707109A patent/EP2111510B1/de active Active
  • 2009-02-19 US US12/918,229 patent/US8398008B2/en active Active
  • 2009-02-19 AT AT09707109T patent/ATE507398T1/de active
  • 2009-02-19 WO PCT/EP2009/051977 patent/WO2009103762A1/de not_active Ceased

Patent Citations (4)

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