WO2010084002A2 - Ensemble machine hydraulique - Google Patents

Ensemble machine hydraulique Download PDF

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Publication number
WO2010084002A2
WO2010084002A2 PCT/EP2010/000345 EP2010000345W WO2010084002A2 WO 2010084002 A2 WO2010084002 A2 WO 2010084002A2 EP 2010000345 W EP2010000345 W EP 2010000345W WO 2010084002 A2 WO2010084002 A2 WO 2010084002A2
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
piston
pump
arrangement according
pressure
Prior art date
Application number
PCT/EP2010/000345
Other languages
German (de)
English (en)
Other versions
WO2010084002A3 (fr
Inventor
Robert Eckert
Thorsten Zellmann
Georg Leutgeb
Franz Wirzberger
Paul Schwab
Sebastien Ambrosetti
Kurt Fassnacht
Jürgen HOEFLING
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2010084002A2 publication Critical patent/WO2010084002A2/fr
Publication of WO2010084002A3 publication Critical patent/WO2010084002A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/1115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members the movement of the pumping pistons in only one direction being obtained by a single-acting piston liquid motor, e.g. actuation in the other direction by spring means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N13/00—Lubricating-pumps
    • F16N13/02—Lubricating-pumps with reciprocating piston

Definitions

  • the invention relates to a hydraulic machine arrangement according to the preamble of patent claim 1.
  • the document JP 11315780 A shows such a hydraulic machine arrangement.
  • This has a piston pump for conveying lubricants for machine tools, wherein the piston pump is designed as a differential cylinder.
  • a piston guided in the cylinder divides it into two cylinder chambers which are each connected to an inlet and an outlet connection.
  • the piston is driven via a piston rod guided outward through the cylinder. In the case of a piston movement, lubricant is sucked in from the inlet connection in the enlarging cylinder space and conveyed to the outlet connection in the decreasing cylinder space.
  • check valves are arranged in the connections.
  • the discharge and inlet connections are connected to each other via pressure medium lines.
  • the piston pump is driven by an additional drive unit connected to the piston rod.
  • Piston rod must be arranged.
  • the invention has for its object to provide a hydraulic machine assembly which is compact with an integrated drive unit. This object is achieved by a hydraulic machine arrangement according to the features of patent claim 1.
  • a hydraulic machine arrangement has at least one motor and at least one pump driven by it.
  • the engine and the pump each have a guided in a cylinder piston.
  • the cylinders and the respective associated piston are movable relative to each other, wherein in the engine and the pump either the cylinder or the piston are movable.
  • the moving components of the motor and the pump are connected.
  • a stroke of the motor is accompanied by a corresponding delivery stroke of the pump, wherein the pump then conveys coolant and / or lubricant.
  • This solution has the advantage that such a hydraulic machine arrangement is extremely ⁇ compact and simple.
  • the engine can advantageously be supplied with pressure medium from the coolant and / or lubricant circuit or this is driven via an already existing hydraulic circuit to be supplied with the coolant and / or lubricant machine tool. Due to the approximately synchronous movement of the cylinders or pistons, the motor and the pump are extremely cheap and easy to tune to each other and the volumetric flow of the motor is directly proportional to the delivered volumetric flow of the pump, whereby a simple control and regulation can take place.
  • the motor and the pump are designed as a synchronous cylinder, whereby the cylinder chambers of the respective cylinder separated from the piston can be essentially the same. Furthermore, such Gleichgangzylinder standard components and thus extremely inexpensive.
  • the pistons are fixed firmly and the cylinders are movable.
  • the pistons of the cylinders have a different piston diameter, wherein the piston area of the piston of the pump can be about twice the size of the piston area of the piston of the engine. In the latter case, a low pressure medium volume flow of the engine can lead to twice the cooling and / or lubricant volume flow.
  • Piston rods of the cylinders are preferably arranged at a parallel distance from one another and, for example, simply held in a frame.
  • the pressure fluid supply and removal device technology extremely cost-effectively implemented if this is done via introduced into the piston rods pressure lines. This is also advantageous because the piston rods are not moving components. The connections for the pressure lines can then be provided over end faces of the piston rods.
  • the pressure lines then open, for example, over end faces of the piston. It may be advantageous if an annular groove in each case in an end face of the piston is introduced approximately concentrically about the longitudinal axis and adjacent to a piston edge and then in each case the pressure line opens into this annular groove. This has the advantage that the pressure medium can be relatively uniformly distributed over the annular groove supplied to the cylinder and the proximity to a cylinder inner wall particle deposits can be removed at this from the inflowing pressure medium.
  • the pressure lines of a cylinder can be introduced either from a piston rod side or from different piston rod sides of the cylinder, whereby different connection possibilities of the pressure lines are made possible.
  • this has an approximately hollow cylindrical see in the cylinder sealingly sliding piston collar, which is supported between two interconnected piston flanges, wherein the piston flanges then each fixed a tubular piston rod is arranged.
  • the pressure lines are guided as pressure tubes respectively through one of the tubular piston rods and in each case at a passage opening connected to a piston flange.
  • the piston rods surrounded by a scraper and a sealing ring.
  • the sealing ring is arranged in relation to the stripping element in the longitudinal direction in each case further out in the passage, which is then prevented by the scraper that particles with the pressure medium reach the sealing ring.
  • a leakage connection can be provided, which advantageously largely leakage from the pump or the engine leaking leakage is avoided.
  • a cylinder position of the cylinder is determined via a displacement measuring system and / or via position sensors.
  • the position sensors can then each measure the final position of the cylinder.
  • the cylinders are arranged coaxially and have a common piston rod, whereby the moving component of the motor, the moving component of the pump moved by mechanical or low pressure or tensile forces.
  • the cylinders are arranged coaxially and have a common piston rod, wherein the cylinder of the engine is designed as a synchronous cylinder, the piston rod projects into the other cylinder.
  • the other cylinder has a cylinder space dividing diaphragm, wherein the piston rod then acts in a direction of displacement of the cylinder to the membrane and with this demarcated from the membrane first cylinder space for cooling and / or lubricant promotion reduced, the second cylinder chamber then with a Tank is connected.
  • Such a hydraulic machine arrangement is very wear-resistant and has an extremely long service life.
  • the cylinder of the pump is moved by mechanically acting in the longitudinal direction of pressure or tensile forces mechanically favorable from the cylinder of the engine.
  • the pressure lines in this engine are incorporated in the cylinder for Druckschzu- and -abbow.
  • the pressure lines of the engine are preferably connected to a directional control valve, wherein via the directional valve then one of the pressure lines with a pump and the other with a tank or both are connected to a tank.
  • the directional valve is a cost-effective standard component.
  • the directional control valve can, for example, control the pressure medium supply of the engine as a function of the position of the cylinders determined by the position sensors or the displacement measuring system.
  • the pressure of the pressure medium can be limited.
  • the directional control valve and / or the pressure limiting valve can be continuously adjustable.
  • three cylinders are provided, with one cylinder being used as the engine and two cylinders as the pump.
  • the volume flow of the pumps is in a fixed relationship to that of the engine, and is e.g. twice as large, with extremely cost essentially identical cylinders can be used.
  • a first cylinder has a piston rod on both sides, which dips with its end portions in each case adjacent to the cylinder cylinder chambers of the second cylinder.
  • the Kotbenstange can be acted upon via their end portions with a pressure force of a pressure in the respective cylinder chamber of the second cylinder in the direction of displacement.
  • a leakage connection for discharge and discharge of leakage as well as for monitoring can be arranged.
  • the cylinders are arranged approximately coaxially with each other and have a common piston rod.
  • At least one guide band is provided on its outer circumference.
  • a coolant and / or lubricant circuit of the pump can easily be up and steuste with a directional control valve.
  • a gas can be supplied to the coolant and / or lubricant, wherein the gas can be supplied, for example, via a gas line connected to the coolant and / or lubricant circuit and Supply via a directional control valve in the gas line and may be zuu Kunststoffbar.
  • gas for example, air is suitable.
  • the motor can advantageously be driven pneumatically, hydraulically or with a coolant and / or lubricant medium, whereby the hydraulic machine arrangement can be used flexibly in a wide variety of pressure medium circuits.
  • FIG. 1a shows a schematic representation of a hydraulic machine arrangement according to a first embodiment
  • Figure 1b shows a detail of the hydraulic machine assembly according to a second embodiment
  • Figure 1c shows a detail of the hydraulic machine assembly according to a third embodiment
  • FIG. 1d shows a section of the hydraulic machine arrangement according to a fourth exemplary embodiment
  • Figure 2 is a longitudinal sectional view of a piston and a cylinder portion of the hydraulic machine assembly according to a fifth embodiment
  • Figure 3 is a longitudinal sectional view of the piston and the cylinder portion of the hydraulic machine assembly according to a sixth embodiment
  • Figure 4 is a longitudinal sectional view of the piston and the cylinder portion of the hydraulic machine assembly according to a seventh embodiment
  • Figure 5 is a longitudinal sectional view of an end-side cylinder portion of the hydraulic machine assembly
  • FIG. 6 is a schematic representation of the hydraulic machine arrangement according to an eighth exemplary embodiment.
  • Figure 7 is a schematic representation of the hydraulic machine assembly according to a ninth embodiment.
  • Figure 8 is a longitudinal sectional view of the hydraulic machine assembly according to a tenth embodiment
  • Figure 9 is a side view of the hydraulic machine assembly of Figure 8.
  • FIGS. 10a to 10d show an enlarged detail of the hydraulic machine arrangement from FIG. 8;
  • Figure 11 is a longitudinal sectional view of the hydraulic machine assembly according to an eleventh embodiment
  • Figure 12 is a longitudinal sectional view of the hydraulic machine assembly according to a twelfth embodiment.
  • FIG. 1 shows a schematic representation of a hydraulic machine arrangement
  • a machine tool 2 with coolant and / or lubricant (KSM).
  • KSM coolant and / or lubricant
  • Such a machine tool 2 is used for example in the machining technology as a milling, turning or drilling machine.
  • the hydraulic machine arrangement 1 has a pump 4, which drives a motor 8 via a 3-way valve 6, which in turn is connected to a pump 10, which conveys coolant and / or lubricant to the machine tool 2.
  • a hydraulic pump 4 which is connected via a pump line 12 to a pump port P of the directional control valve 6.
  • a throttle 14 is provided in the pump line 12.
  • the directional control valve 6 further has a tank connection T connected to a tank line 16, the tank line 16 being connected to a tank 18 via an adjustable flow control valve 17.
  • the directional control valve 6 With working ports A and B, the directional control valve 6 is connected to working lines 20 and 22 of the motor 8.
  • a valve spool of the directional control valve 6 is centered via two springs 24, 26 in a basic position 0 and can be brought via lifting magnets 28, 30 in the figure 1a to the right in the switching position a and to the left in the switching position b.
  • the working lines 20, 22 are connected to the tank line 16.
  • the pump line 12 with the working line 22 and the working line 20 with the tank line 16 and reversed in the switching position b the working line 20 to the pump line 12 and the working line 22 is connected to the tank line 16.
  • pressure relief valve 34 is connected, wherein the applied pressure in this pressure via a pressure gauge 35 can be tapped.
  • pressure medium This is designed as a synchronous cylinder 8, in which a piston 36 is slidably guided. From the cylinder 8 projects on both sides of a piston rod 38 which is fixed in a frame 40.
  • the pump 10 which is likewise designed as a synchronous cylinder 10, is arranged substantially parallel to the cylinder 8, with a piston rod 44 of the cylinder 10 connected to a piston 42 also being fixedly connected to the frame 40.
  • the frame 40 has a base plate 46 connected to the lower end portions of the piston rods 38, 44 in FIG. 1 a, which is formed as a leak oil pan, and a cover plate 48 connected to the upper end portions.
  • the frame 40 is further provided with a protective cover 50 ,
  • the Gleichgangzylinder 8, 10 have approximately the same axial length and are firmly connected together at the same height.
  • the pressure medium supply and removal of the cylinders 8 and 10 takes place via respectively introduced into the piston rods 38 and 44 pressure lines 52, 54 and 56, 58.
  • the pressure lines 52, 54 and 56, 58 are each of a common end face 60 and 62 of the piston rods 38 and 40 introduced as axial bores forth, each in a connected to a respective annular space of the cylinder 8 and 10 and introduced into the piston rods 38 and 40 radial bores open.
  • the radial bores are each introduced close to the piston, whereby a high cylinder stroke is possible.
  • the working line 22 and to the pressure line 54, the working line 20 is connected in each case from the end face 60 of the piston rod 38 ago.
  • the pressure line 56 and 58 of the pump 10 is connected to each other as in the engine 8 with a pressure line 64 and 66 on the end face 62 of the piston rod 44.
  • the pressure lines 64 and 66 are then on a supply line line 68 and a drain line string 70 for a coolant and / or lubricant (KSM) in Druckstoffverbin- cerg.
  • the supply line branch 68 has two inlet sections 72 and 74, which are each connected to the pressure line 64 and 66, respectively.
  • the drain line 70 has two drain sections 76 and 78 which are also in communication with the pressure lines 64 and 66, respectively.
  • a check valve 80, 82, 84, 86 is arranged in each case.
  • the check valves 80 and 82 of the supply line branch 68 open respectively
  • the check valves 84 and 86 of the drain line string 70 close to the pressure lines 64 and 66, respectively.
  • the coolant and / or lubricant connection in the supply line branch 68 is ascendable and controllable via a 2-way valve 88 to a coolant and / or lubricant source 90.
  • a valve body of the directional control valve 88 is biased in a basic position 0 with a spring 92 in which the cooling and / or lubricant connection is interrupted.
  • Via a solenoid 94 the directional control valve 88 is switchable into an open position a.
  • an adjustable throttle valve 95 is arranged between the directional control valve 88 and the source 90.
  • the drain line string 70 is further connected to a rotary distributor 96 of the machine tool 2.
  • the machine tool 2 has a tool spindle 98 and a tool clamp 100 with which a tool 102 is tensioned.
  • a supply line 104 is connected to the drain line strand 70 and supplies the coolant and / or lubricant to the tool 102.
  • the tool clamp 100 is, for example, also operable with the hydraulic circuit of the motor 8.
  • position sensors 106, 108 are arranged, with which a reaching of the two end positions of the composite of motor 8 and pump 10 can be seen.
  • the cylinder 8 is shown in a lower position, which is reported by the position sensor 108, for example, to an engine control, not shown, which then switches the directional control valve 6 in the switching position a.
  • an upper annular space 110 of the cylinder 8 in FIG. 1 a with the pump 4 and a lower annular space 112 with the tank 18 are brought into fluid communication, the pump 4 conveying pressure medium into the upper annular space 110.
  • Due to the enlarging annular space 110 of the cylinder 8 is moved in the figure 1a upwards, wherein the cylinder 10 is moved.
  • An enlarging upper annular space 114 of the cylinder 10 sucks in coolant and / or lubricant (KSM) via the pressure line 64, the inlet section 72 and the inlet line line 68 from the coolant and / or lubricant source 90.
  • KSM coolant and / or lubricant
  • the solenoid 96 of the directional control valve 88 is energized and thus is a valve body of the directional control valve 88 in an open position a.
  • a decreasing annular space 116 of the cylinder 10 then displaces KSM via the pressure line 66, the discharge section 78 and the discharge line line 70 to the machine tool 2. If the cylinders 8, 10 then reach the upper position in FIG.
  • the piston 42 of the cylinder 10 has a larger, substantially twice as large pressure application surface, as the piston 36 of the cylinder 8.
  • the KSM volume flow is about twice and the KSM pressure half as large as the flow and pressure of the engine 8 driving pressure medium.
  • the hydromachine arrangement 1 Due to the direct coupling of the motor 8 and the pump 10, the hydromachine arrangement 1 has a very low power loss. By this arrangement, the heat flow from the hydraulic circuit to the KSM circuit is also very low.
  • the hydraulic circuit for driving the motor 8 can advantageously also be used for the machine tool 2, as a result of which the outlay in terms of technical equipment can be considerably reduced.
  • the hydraulic machine assembly also has a high robustness and a functionally reliable construction and has shown in use to be extremely quiet.
  • a position measuring system for determining the position of the cylinders 8, 10 in the hydraulic machine arrangement can be arranged. This has a fixed to the cylinder 8 distance sensor 120, which measures the distance to a rail 40 mounted on the rail 122. This is inclined with respect to the piston rods 38, 40, so that the distance during a lifting movement the cylinder 8, 10 changed to the distance sensor 120, whereby the current position 8, 10 can be determined.
  • FIG. 1b shows the directional control valve 6 from FIG. 1a of the hydraulic machine arrangement 1 according to a second exemplary embodiment.
  • This is in contrast to the directional control valve 6 of Figure 1a continuously adjustable, whereby the pressure medium flow to the engine and thus the pump is variable depending on the cooling and / or lubricant requirement of the machine tool 2 adjustable.
  • the pressure medium volume flow is 0 to 25 l / min.
  • FIG. 1 c discloses the directional control valve 6 with the pressure limiting valve 34 of the hydraulic machine arrangement 1 from FIG. 1 a according to a third exemplary embodiment.
  • the difference from the previous exemplary embodiments lies in the fact that in FIG. 1c, in addition, the pressure limiting valve 34 can be adjusted continuously via a lifting magnet 124.
  • the maximum pressure can also be changed.
  • the pressure can be between 10 and 50 bar, for example.
  • FIG. 1d shows a directional control valve 6 according to a fourth embodiment.
  • no Dr ⁇ ckbegrenz ⁇ ngsventil 34 is connected between the pump 4 and the directional control valve 6.
  • the directional control valve 6 is flexible via a control electronics 126, 127 controllable.
  • valve arrangements described in the preceding figures are, for example, simple and compact in the housing 40 can be integrated.
  • the essential valves for the use of the hydraulic machine assembly 1 of Figure 1a are advantageously arranged only in the hydraulic circuit.
  • FIG. 2 shows in a longitudinal sectional view a cylinder cutout with the piston 42 of the cylinder 10 from FIG. 1 a according to a fifth exemplary embodiment of the hydraulic machine arrangement 1.
  • the pressure lines 56, 58 are introduced in the longitudinal direction of the piston rod 44 from one side in a parallel distance, for example, as an axial bore and each end approximately in the region of the piston 42nd With the annular spaces 114 and 116 of the cylinder 10, the respective pressure lines 56 and 58 via at least one introduced into the piston 42 oblique bore 128 and 130 in pressure medium connection.
  • the oblique bore 128 extends from a left in Fig.
  • the oblique bores 128 and 130 do not open directly into the end faces 132 and 134, respectively, but each into annular grooves 136 and 138 introduced therein. These are formed approximately concentrically around the longitudinal axis of the cylinder 10. Through the annular grooves 136 and 138 pressure fluid from the oblique bores 128 and 130 radially evenly into the annular space 114 and 116 can be introduced. In this case, it is advantageous if the annular grooves 136, 138 have a narrow or narrow cross-section, so that the pressure medium can be radially distributed better in them.
  • FIG. 3 shows in a longitudinal sectional view a cylinder cutout with the piston 42 of the cylinder 10 from FIG. 1 a according to a sixth exemplary embodiment of the hydraulic machine arrangement 1.
  • the piston 42 here has oblique bores 128, 130, as in FIG. 2, although the pressure lines 56, 58 are introduced into the piston rod 44 from different sides.
  • the pressure line 58 extends in the figure 3 from the left and the pressure line 56 from the right approximately coaxial with the center axis of the piston rod 44 each to the corresponding oblique bore 130 and 128 respectively.
  • FIG. 4 in a longitudinal sectional view, as in FIGS. 2 and 3, the cylinder cutout with the piston 42 of the cylinder 10 from FIG. 1 a according to a seventh exemplary embodiment of the hydraulic machine arrangement 1 is also disclosed.
  • the piston 42 and the piston rod 44 are in this case constructed in several parts.
  • An approximately hollow cylindrical piston collar 150 is fixedly clamped between two mutually connected piston flanges 152, 154 (for example by a screw connection), the radial circumferential wall 156 of the piston flanges 152, 154 and the piston collar 150 slidingly abutting against the inner wall 140 of the cylinder 10.
  • two countersunk bores 158, 160 are provided, which are designed such that, for example, a nut can connect the flanges 152, 154 with a screw.
  • the screw connection is surrounded between the flanges 152, 154 each with a tubular sealing body 162, 164.
  • the piston rod 44 is formed with two tubular piston rods 166, 168, which are inserted into recesses of the end faces 132, 134 of the piston flanges 152, 154 and fixedly connected to the piston flanges 152, 154.
  • the connection is made for example by laser welding or soldering.
  • At the center of the piston flanges 152, 154 is an provided passage bore through which in each case in the piston rods 166, 168 arranged tubular pressure lines 170, 172 are passed.
  • the pressure lines 170 and 172 are then connected in each case to through holes 174, 176 introduced obliquely into the piston flanges 152, 154, the through bores 174, 176 opening into annular grooves 136, 138, as in the previous exemplary embodiments.
  • FIGS. 1a, 2, 3 and 4 are coated with a wear-resistant surface protection in order to achieve a long service life.
  • FIG. 1 a the cylinder 10 is described.
  • the cylinder 8 from FIG. 1 a can be configured in the same way as the embodiments shown with reference to the cylinder 10.
  • the different embodiments may be different for the cylinders 8, 10, respectively.
  • FIG. 5 shows in a longitudinal sectional view a passage 178 of the piston rod 44 through the cylinder 10 of the hydraulic machine arrangement 1 from FIG. 1a.
  • the upper annular space 114 in FIG. 1a is arranged on the right in FIG.
  • a stripping element 180 encompassing the piston rod 44 is inserted, which serves to scrape off abrasive particles on the piston rod 44.
  • a sealing ring 182, which prevents pressure medium leakage of the cylinder 10, is provided on the left in the bushing 178, that is, further away from the annular space 114 than the stripping element 180.
  • a leakage connection 184 is introduced radially in the passage 178. This leads between the stripping element 180 and the sealing ring 182 arising from leakage. At this a transparent leakage line can be connected as a wear indicator, whereby the leakage amount is visible and the state of the scraper element 180 and the sealing ring 182 can be estimated.
  • the described passage 178 is provided for the entire end portions of the cylinders 8, 10 of FIG. 1a. Due to the robust construction of the hydraulic machine arrangement 1 from FIG. 1 a, fine filtering of the coolant and / or lubricant during the return from the machine tool 2 is no longer necessary.
  • FIG. 6 shows, in a longitudinal sectional view, the motor 8 and the pump 10 according to an eighth exemplary embodiment. These are arranged approximately coaxially and have a common piston rod 186 which is connected to the piston 36 of the motor 8 and projects into the cylinder 10. On the one hand, according to FIG. 1a, the piston rod 186 can be fixed, or the cylinders 8, 10. The piston rod 186 is intended to be fixed in the following.
  • a rod end section 187 of the piston rod 186 which projects into the cylinder 10 presses on a membrane 188 introduced into the cylinder 10.
  • This is provided with a retaining collar 190 between a cylinder cover 192 and a radially stepped back from inside End portion 194 of the cylinder 10 is supported and divides the cylinder 10 in a connected to a tank bar space 196 and a diaphragm space 198.
  • the membrane space 198 is in pressure-fluid connection with the coolant and / or lubricant source 90 or the machine tool 2 in a manner not shown.
  • the rod end section 187 moved by the movement of the cylinder 8 in the direction of the membrane 188 reduces the membrane space 198 by compressing the membrane 188 and delivers coolant and / or lubricant via the pressure medium connection 200 to the machine tool 2 from FIG.
  • the motor 8 is driven in accordance with as described in Figure 1a, in which case, however, the pressure medium supply to the annular spaces via the cylinder 8 takes place.
  • the rod end portion 187 is radially expanded to achieve a larger contact surface 201 on the membrane 188. This has an approximately flat attack surface 203.
  • the arrangement described in FIG. 6 is characterized in particular by the fact that the KSM in principle leads to no abrasion on the motor 8 and the pump 10, whereby the wear of the motor 8 and pump 10 is minimized.
  • FIG. 7 shows, in a simplified schematic illustration, the hydraulic machine arrangement 1 from FIG. 1 a according to a ninth exemplary embodiment. This has here the directional control valve 6 of Figure 1d.
  • the drain line string 70 is additionally up and steuste with a directional control valve 202 to the machine tool 2.
  • the coolant and / or lubricant (KSM) in the exemplary embodiment additionally gas in the form of air can be supplied.
  • KSM coolant and / or lubricant
  • a gas line 204 branched off from the feed line branch 68 is provided which can be connected to a gas source 208 via a directional control valve 206.
  • the connection to the gas source 208 is openable and controllable, wherein in the switched-off state, the gas line 204 is vented via the directional control valve 206.
  • an adjustable throttle valve 210 is arranged between the directional control valve 206 and the gas source 208 is still.
  • a check valve 211 opening toward the delivery line 68 is provided in the gas line 204.
  • Another check valve 213 is disposed between the directional control valve 88 and the branch point of the gas line 204, which also opens to the supply line line 68.
  • FIG. 8 is a longitudinal sectional view of the hydraulic machine assembly 1 according to a tenth embodiment. In contrast to the preceding exemplary embodiments, these three cylinders 216, 218 and 220 have the middle cylinder 218 in FIG.
  • the cylinders 216, 220 are designed substantially identical. As in the case of the first exemplary embodiment from FIG. 1a, the cylinders 216 to 220 are arranged approximately parallel to one another.
  • the cylinders 216, 218 and 220 are designed as a Gletchgangzylinder and each have a piston rod 222, 224 and 226 on. About this a piston 228, 230 and 232 in a cylinder tube 234 of the cylinder 216 to 220 is guided in each case.
  • the piston rods 222, 224 and 226 pass through a respective cylinder head 242, 244 and 246 of the cylinders 216, 218 and 22O, respectively, with their end portions 236, 238 and 240 arranged on the right by the respective piston 228, 230 and 232 in FIG.
  • the end sections 236, 238 and 240 are radially stepped back at their end region 247 facing away from the respective piston 228, 230 and 232, respectively, and are in each case passed through a passage opening 248 of a jointly defined retaining plate 250.
  • the end regions 247 of the end sections 236, 238 and 240 then rest against an underside 252 of the retaining plate 250 facing the cylinders 216 to 220 with an annular end face.
  • the end regions 247 furthermore have a thread on which a respective nut 254 is screwed, which in each case is supported on an upper side 256 of the retaining plate 250 and clamps the annular end faces of the end regions 247 against the underside 252.
  • a lock nut 258 is screwed on the end portions 247 of the end portions 236-240.
  • cylinder tubes 234 are each tensioned via a conventional tie rod connection 270 between the cylinder bottom 268 and the respective cylinder head 242, 244 and 246, respectively.
  • tie rod connection For further information regarding the construction of a tie rod connection reference is made to the book "The Hydraulic Trainer, Volume 1", 3rd revised edition of the company Bosch Rexroth AG.
  • the piston rods 222 to 226 are each constructed in two parts, wherein a part of the respectively in the figure 8 right end portion 236 to 240 and the other part of the left Endab- is 260-264.
  • the exact structure of the piston rods 222 to 226 together with the pistons 228 to 232 will be explained in more detail with reference to the lower cylinder 220 in FIG.
  • the piston 232 has a through opening 272 which extends approximately coaxially with respect to its longitudinal direction. End regions 274 and 276, respectively, of the end sections 264 and 240 facing the piston 232 are radially stepped back, their diameter being approximately equal to that of FIG.
  • Diameter of the passage opening 272 of the piston 232 corresponds.
  • the end portions 274, 276 are immersed in the through hole 272 of the piston 232 and fixedly connected to each other, for example via a screw, the piston 232 between ring end faces of the radiallyteilzustuften end portions 274, 276 is firmly clamped.
  • the pistons 228 to 232 each separate a left annulus 278 from a right annulus 280 of the cylinders 216 to 220.
  • the right annulus 280 is shown in Figure 8 with minimal volume.
  • the pressure medium supply of the cylinder used as a motor 218 and the KSM supply of the cylinder used as a pump 216, 220 takes place, for example, as in Figures 1a, 2, 3, 4 and 7 via the piston rods 222 to 226. It is also possible to Cylinder 216 to 220 to supply via the cylinder bottom 268 and the respective cylinder head 242 to 246 with pressure medium or KSM, which is not shown in the figure 8.
  • the cylinder 218 is connected, for example, to the working lines 20 and 22 from FIG. 1a, while the cylinders 216 and 220 are in KSM connection with the pressure lines 64, 66.
  • FIG. 9 shows the hydraulic machine arrangement 1 from FIG. 8 in a side view.
  • the pressure medium or KSM supply of the cylinder heads 242 to 246 is shown in FIG. 8, which is briefly explained on the basis of the cylinder head 246.
  • the cylinder head 246 has a pressure port 282 to which a pressure line 284 is connected, which in turn communicates with a pressure port 286 of the cylinder bottom 268.
  • the right in the Figure 8 annulus 280 of the cylinder 220 is thus connected via channels in the cylinder head 246 to the pressure port 282 and connected via this with the pressure line 248 to the pressure port 286 of the cylinder bottom 268.
  • the pressure port 286 is then connected to channels for pressure medium or KSM supply, which are formed in the cylinder bottom 268 connected.
  • pressure is alternately applied in the annular spaces 278 and 280 of the motor used as a motor Cylinder 218 built. If, in the position of the cylinders 216 to 220 shown in FIG. 8, pressure medium is conveyed into the right-hand annular space 280 of the middle cylinder 218, it is acted upon by a pressure force via the cylinder head 244 in the direction of the retaining plate 250. Together with the cylinder head 244, the bottom plate 268 and via this the other two cylinders 216, 220 are also moved in the direction of the holding plate 250.
  • the cylinder 218 used as a motor has damping bushes 288 and 290, respectively. These are each arranged on a radially stepped-back region of the end sections 238, 262 of the piston rod 224. A diameter of the radially stepped-back region is larger than the diameter of the through-opening 272 of the piston 230. The reclassified region follows directly the likewise radially recessed end section 274, 276 (see cylinder 220).
  • the damping bushings 288, 290 are thus respectively tensioned between an annular end face of the piston 230 and an annular surface of the end section 238 or 262 formed by the radial downgrading.
  • the left in the figure 8 Dämpf ⁇ ngsbuchse 288 emerges at the end of the lifting movement of the cylinder 218 in an introduced into the cylinder bottom 268 of the annulus 278 ago bore 292 a. This limits together with the end portion 262 of the piston rod 224 an annular space.
  • the diameter of the bore 292 is larger than the diameter of the damping bush 288 chosen so that when dipping the damping bushing 288 in this bore 292 between an inner wall of the bore 292 and an outer wall of the damping bushing 288 a circumferential gap is formed. This serves as a throttle of between the limited by the bore 292 annulus and the annulus 278.
  • the right in Figure 8 damping bushing 290 immersed in an introduced into the cylinder head 244 bore. The mode of operation here is according to the left damping bushing 288.
  • FIGS. 10a-10d show enlarged sections of the hydraulic machine arrangement 1 from FIG. 8.
  • FIG. 10 a shows a section I which shows the passage of the end section 260 of the piston rod 222 from FIG. 8 through the passage opening 266 of the cylinder bottom 268.
  • the cylinder bottom 268 has in the region of the passage opening 266 a stripping element 294, two sealing elements 296, 298 and a guide collar 300.
  • the elements 294 to 300 are spaced apart from one another in the longitudinal direction of the passage opening 266, with the guide collar 300 being arranged closest to the annular space 278 from FIG.
  • the elements 294 to 300 are each inserted into a coaxial with a longitudinal axis of the passage opening 266 introduced annular groove.
  • the annular grooves are introduced into the cylinder bottom 268 from an inner lateral surface of the through-opening 266.
  • the stripping element 294 is of annular design and comprises the end section 260. With a stripping lip 302, this abuts against an outer circumferential surface 304 of the end section 260, as a result of which dirt particles are scraped off over the latter. Stripped dirt particles can then be removed from the cylinder bottom 268 via the passage opening 266 to the outside, to the left in FIG. 10a. For easier removal of the removed particles, the passage opening 266 between the stripping element 294 and a left outer surface 306 of the cylinder bottom 268 is radially expanded.
  • the stripping element 294 has on its side facing away from the wiper lip 302 side a ring recess, between which and the annular groove of the cylinder bottom 268, an O-ring 308 is inserted. This is formed in such a way that the wiper lip 302 of the wiping element 294 is stretched over the wiper surface 304 of the end section 260.
  • the sealing elements 296, 298 are also annular and engage around the end portion 260. These have in each case a sealing lip 310, 312, which bears sealingly against the lateral surface 304 of the end portion 260.
  • the sealing lips 310, 312 in each case have an encircling inclined surface which extends from the lateral surface 304 of the end portion 260 in the direction of the outer surface 306 of the cylinder bottom 268. Furthermore, the sealing lips 310, 312 have a guide surface 300 facing approximately perpendicular to the longitudinal axis of the end portion 260 extending annular surface.
  • the sealing elements 296 and 298 are respectively encompassed by an O-ring 314 or 316 accommodated in the annular groove of the cylinder bottom 268.
  • the O-rings 314 and 316 then respectively clamp the sealing elements 296 and 298 with the sealing lips 310 and 312 against the lateral surface 304 of the end portion 260, whereby a high sealing effect is achieved.
  • the KSM conveyed by the cylinder 216 is only conditionally suitable for lubricating the moving parts of the cylinder 216.
  • the annular guide collar 300 is provided in order to prevent wear between the end section 260 of the piston rod 222 and the passage opening 266 of the cylinder bottom 268, the annular guide collar 300 is provided. This has a smaller inner diameter than the through hole 266 and surrounds the end portion 260. The end portion 260 is thus guided over the guide collar 300 and not via an inner wall of the through hole 266.
  • the guide collar 300 consists of a material that a wear of the end portion 260th essentially prevented.
  • the arrangement of the stripping element 294, the sealing elements 296, 298 and the guide collar 300 described in FIG. 10a are configured correspondingly in the cylinder head 242 from FIG. 8, whereby they are arranged in the reverse order.
  • the lower cylinder 220 in FIG. 8 is designed accordingly.
  • FIG. 10b shows an enlarged section II of the hydraulic arrangement 1 from FIG. 8.
  • the passage region of the end section 262 of the piston rod 224 of the middle cylinder 218 in FIG. 8 is shown in sections through the cylinder bottom 268.
  • a stripping element 322 and a sealing element 324 are inserted from the passage opening 266.
  • the sealing element 324 is arranged closer to the annular space 278 of Figure 8.
  • the stripping element 322 has a holding section 328 inserted into the annular groove 318 and a lip section 330 projecting approximately in the longitudinal direction into the through-hole 326. The latter is stretched over its residual stress with an inner surface against the lateral surface 304 of the end section 262.
  • the sealing element 324 is a grooved ring, which surrounds the end section 262 in a sealing manner with a sealing lip 332.
  • the cylinder head 244 of the cylinder 218 also has the elements 322, 324, which are formed and arranged accordingly, but in reverse order.
  • FIG. 10c shows an enlarged detail III of the hydraulic machine arrangement 1 from FIG. 8.
  • the guidance of the upper piston 228 in FIG. 8 is shown in the cylinder tube 234 of the cylinder 216.
  • the piston 228 are from its substantially a circular cylindrical cross-section having outer circumferential surface 334 ago three in
  • annular groove 338 Longitudinal direction of the piston 228 spaced annular grooves 336, 338 and 340 introduced.
  • the annular groove 338 is arranged centrally between the annular grooves 336 and 340, wherein the two latter are configured substantially equal.
  • a guide collar 342, 344 is used, which correspond to the guide collar 300 of Figure 10a.
  • the function of the guide collars 342, 344 corresponds to that of the guide collar 300.
  • two O-rings 348, 350 are inserted, wherein these are arranged in the radial direction one behind the other and the O-ring 348 sealingly abuts an inner circumferential surface 346 and the O-ring 350 between a groove bottom of the annular groove 338 and O-ring 348 is arranged.
  • the O-rings 348, 350 serve to substantially fluid-tight separation of the annular spaces 278, 280 of the cylinder 216 of Figure 8.
  • the piston 232 of the cylinder 220 is designed accordingly.
  • FIG. 10d shows a section IV of the hydraulic machine arrangement 1 from FIG. 8 enlarged.
  • a portion of the piston 230 and the cylinder tube 234 of the cylinder 218 is shown.
  • guide collars 352, 354 are used which have approximately half the axial length in comparison to the guide collars 342, 344 from FIG. 10c. Ring grooves in which the guide collars 352, 354 are used are formed correspondingly smaller.
  • FIG. 11 is a longitudinal sectional view of the hydraulic machine assembly 1 according to an eleventh embodiment.
  • This is designed as a so-called in-line arrangement and in this case has three chambers 358, 360 and 362 formed in a machine housing 356.
  • a piston 364 is guided with a piston rod 366.
  • This fully penetrates the about a circular cylindrical cross-section having chamber 360, whereby it is separated from the piston 364 and the piston rod 366 in two annular chambers 368, 370.
  • the piston rod 366 cantilevers on both sides of the Ring chambers 368, 370, each having an end portion 372, 374 of and in the adjacent to the chamber 360 arranged chambers 358 and 362 a. These also have an approximately circular cylindrical cross-section and are arranged coaxially with the chamber 360.
  • the annular chambers 368 and 370 are a first cylinder and the chambers 358, 362 a second cylinder assignable.
  • the left-hand chamber 358 in FIG. 11 is connected to the working line 20 from FIG. 1 a and the right-hand chamber 362 is connected to the working line 22.
  • the left in Figure 11 annular chamber 368 is connected to the pressure line 64 and the right annular chamber 370 with the pressure line 66 (of Figure 1a).
  • a leakage connection 184 is provided which corresponds to that of the figure 5a equivalent.
  • sealing elements are provided in a respective through hole 380 and 382 of the partition walls 376 and 378 through which the end portions 372 and 374 are passed.
  • the cylinder with the chambers 358 and 362 serves as a motor, wherein the piston rod 366 is applied alternately either from the chamber 358 or from the chamber 362 with a pressing force of the pressure medium.
  • a pressure force acts on its end face 384 of the left-hand end section 372.
  • KSM is displaced from the right annular chamber 370 via the piston 364, while KSM is sucked in via the left annular chamber 368.
  • a compressive force to move the piston rod 366 in the figure. 11 to the left acts on a face 386 of the end portion 374 via the chamber 362 a compressive force.
  • annular chambers 368 and 370 are connected to the pressure medium and the chambers 358, 362 to the KSM.
  • FIG. 12 shows a twelfth exemplary embodiment of the hydraulic machine arrangement 1 shown in a longitudinal section view.
  • two cylinders 388, 390 arranged approximately coaxially with each other. These are connected via a common cylinder bottom 391, which is penetrated by a common piston rod 392 approximately coaxially.
  • the cylinders 388 and 390 each have a cylinder tube 394 and 396, respectively.
  • Into the respective cylinder derrohr 394 and 396 emerges a approximately circular cylindrical cross-section having projection 398 and 400 of the cylinder bottom 391 each with an O-ring sealing.
  • the cylinder tubes 394 and 396 each sealed with a cylinder head 402 and 404.
  • a piston 406 and 408 connected to the piston rod 392 is slidably guided.
  • the pistons 406 and 408 together with the piston rod 392 form a cylinder with a one-sided piston rod.
  • a left-hand piston 406 in FIG. 12 a left-hand cylinder space 410 is separated from a right-hand annular space 412 of the cylinder 388, while a left-hand annular space 414 is separated from the right-hand cylinder space 416 of the cylinder 390 by the right-hand piston 408 in FIG.
  • a plurality of annular sealing elements 420 are arranged in a through opening 418 of the cylinder bottom 391, through which the piston rod 392 is guided.
  • each piston 406 and 408 likewise has an annular sealing element on its outer side facing the respective cylinder tube 394 or 396.
  • the right-hand cylinder 390 in FIG. 12 is connected to the working lines 20, 22 from FIG. 1 a and the left-hand cylinder 388 to the pressure lines 64, 66.
  • the piston 408 With a constant pressure medium volume flow, the piston 408 is displaced in the annular space 414 at a higher speed in the longitudinal direction than in a pressure medium conveying in the cylinder chamber 416 at a Druckschförde- with a displacement of the piston 408 in the figure 12 to the right from the annular space 412th of the cylinder 388 displaced via the piston 406 pressure medium.
  • pressure medium is displaced via the piston 406 from the larger cylinder space 410.
  • a KSM volume flow is thus approximately the same in both directions of displacement of the piston 406, since, when the piston 406 is displaced to the right, the latter is displaced faster, but less KSM is displaced by the annular space 412 having a smaller volume than the cylinder space 410. With a shift of the piston 406 to the left more KSM is displaced from the cylinder chamber 410 in comparison to the smaller annular space 412, but also the piston 406 is displaced at a lower speed.
  • the cylinders 388 and 390 have different diameters in FIG. 12, with the cylinder 388 having a diameter approximately twice as large as the cylinder 390. As a result, at a certain pressure medium volume flow, which drives the cylinder 390 used as a motor, a significantly larger KSM volume flow of the cylinder 388 used as the pump takes place.
  • Cylinder 390 to connect to KSM lines.
  • the motor 8 of Figure 1a, 7, 11 and 12 can be driven pneumatically, with the KSM or by electric motor.
  • An electromechanical control could be done via a rack / threaded spindle / ball screw in conjunction with a speed-controlled electric motor.
  • a hydraulic machine arrangement with at least one motor and at least one pump driven by this.
  • the engine and the pump each have a piston guided in a cylinder.
  • the cylinders and the respective associated piston are movable relative to each other, wherein in the engine and the pump either the cylinder or the piston are movable.
  • the moving components of the motor and the pump are connected.
  • a stroke of the motor is accompanied by a corresponding delivery stroke of the pump, wherein the pump then conveys coolant and / or lubricant.
  • Coolant and / or lubricant source 92 spring

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Ensemble machine hydraulique qui comporte au moins un moteur et au moins une pompe entraînée par ledit moteur. Le moteur et la pompe comportent chacun un piston guidé dans un cylindre. Les cylindres et leur piston associé sont mobiles l'un par rapport à l'autre, et soit le cylindre, soit le piston est mobile dans le moteur et dans la pompe. Les pièces mobiles du moteur et de la pompe sont reliées. Par conséquent, une course du moteur entraîne une course de refoulement correspondante de la pompe, la pompe refoulant alors un agent de refroidissement et / ou un lubrifiant.
PCT/EP2010/000345 2009-01-22 2010-01-21 Ensemble machine hydraulique WO2010084002A2 (fr)

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DE102009005817 2009-01-22

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WO2010084002A3 WO2010084002A3 (fr) 2011-04-14

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Cited By (1)

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US10508960B2 (en) 2013-12-20 2019-12-17 Aktiebolaget Skf Load determining system for a rolling element bearing

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CZ305091B6 (cs) * 2012-07-24 2015-04-29 Emil Brabec Zařízení dávkování tekutin, zvláště pro maziva centrálních systémů ztrátového mazání
DE102014212201A1 (de) * 2014-06-25 2015-12-31 Robert Bosch Gmbh Hydrostatische Maschine
CN111336083A (zh) * 2020-03-09 2020-06-26 嘉兴考普诺机械科技有限公司 一种机床加工用的液压油泵

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DE2741024A1 (de) * 1977-09-12 1979-03-22 Wilms Gmbh Membranpumpe
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Publication number Priority date Publication date Assignee Title
US10508960B2 (en) 2013-12-20 2019-12-17 Aktiebolaget Skf Load determining system for a rolling element bearing

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WO2010084002A3 (fr) 2011-04-14

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