Patent Application
20200408227
This application claims priority from Application No. DE 10 2019 209 440.6 filed Jun. 28, 2019, the entire content of which is incorporated herein by reference.
The present invention relates to a hydromechanical linear converter comprising a cylinder, a piston unit movable relative thereto and a valve unit, wherein the cylinder and a piston of the piston unit define a hydraulic working chamber into which a working connection and a further fluid connection open, wherein the fluid connection communicates hydraulically with the valve unit, which is configured as a seat valve unit having a supply connection and being switchable between a first switching position connecting the supply connection to the fluid connection and a second switching position blocking the fluid connection relative to the supply connection.
Such hydromechanical linear converters are known in various configurations and are used in particular in hydraulic machine presses and plastic injection moulding machines. DE 10 2016 118 853 B3, for example, is relevant in this respect, from which in particular the function of a hydromechanical linear converter within an electrohydraulic drive unit results and to which reference is made and referred to in order to avoid unnecessary repetition.
Hydromechanical linear converters of the concerned type have proven themselves in practical use. Pressing processes, plastic injection moulding processes or similar, as they are made possible by machines with such linear converters, are characterised, for example, by excellent reproducibility and thus high manufacturing quality with a high degree of energy efficiency. The economic efficiency of the respective machine presses, plastic injection moulding machines or the like is influenced not only by the factors just mentioned, but also by the possible short cycle times.
It is therefore one of the characteristics of such hydromechanical linear converters that the piston of the hydromechanical linear converter is moved in a so-called rapid traverse as well as in a so-called power traverse within a working cycle. In the power traverse, the hydraulic working chamber is pressurized with hydraulic fluid by, for example, a hydraulic pump in its pumping mode, whereby high forces can be exerted on the piston, which—depending on the application of the hydromechanical linear converter—can be used to act on workpieces or machine components in the desired manner. In rapid traverse, on the other hand, the focus is not on exerting large forces on the workpiece or a machine component, but, with a view to reducing cycle times, on moving the piston unit quickly. For this purpose, the piston unit is moved by suitable external forces (for example the weight of the piston unit or a tool connected to it or an auxiliary drive acting on the piston unit) and by switching the valve unit to the first switching position, it is possible for hydraulic fluid to flow into or out of the hydraulic working chamber via the valve unit and its supply connection, depending on the direction of movement of the piston unit.
It is the object of the present invention to provide a hydromechanical linear converter which has been further improved in terms of economy, energy efficiency, compactness and the possibilities of process optimization.
This object is solved by using a hydromechanical linear converter of the type mentioned above, where the valve unit comprises
In the linear converter according to the invention, mechanical, electromagnetic as well as hydraulic effects are used for switching and hydraulically shutting off the fluid connection from the supply connection (including holding the respective second switching position). In interaction, the spring unit and the electromagnetic actuator—depending on its electrical loading—move the valve body into the first or the second of the two switching positions, but in the second switching position a hydraulic force, which acts on the valve body from the hydraulic operating chamber, ensures that the valve head is in sealing contact with the valve seat, thus enabling the fluid connection to be reliably shut off from the supply connection even at high pressures in the hydraulic working chamber of the linear converter. The said hydraulic operating chamber (also) communicates through the compensation channel when the valve unit—with the valve head in contact with the valve seat—is in the second switching position, which shuts off the fluid connection from the supply connection. As a result, such a pressure—adjusted to the pressure conditions in the hydraulic working chamber of the linear converter—builds up in the hydraulic operating chamber, which causes the valve body to be hydraulically self-retaining, so that the second switching position is reliably maintained even when the electromagnetic actuator is currentless.
In a surprisingly simple way, this contributes to a substantially improved usability of the hydromechanical linear converter compared to the prior art, as the economic efficiency, the energy efficiency, the compactness as well as the possibilities of process optimization can be improved at the same time:
According to a first preferred embodiment of the invention, the valve housing comprises a base body and a pot-shaped insert disposed therein, which forms the valve seat and has at least one peripheral opening. In this configuration, the advantage of compactness is particularly pronounced. Furthermore, due to the ruggedness of the configuration, this embodiment has advantages with regard to the service life of the hydromechanical linear converter. Preferably, the base body is a multi-part element, preferably two-part element, with a base structure comprising the fluid connection and supply connection and a cover. To a certain extent, the insert can be clamped between the base structure and the cover. This makes the valve unit particularly easy to manufacture and install, which has a positive effect on manufacturing, assembly and maintenance costs.
The valve body described above is preferably sealingly guided in the insert. In this way, the sealing of the hydraulic operating chamber can be achieved very economically without the use of further components.
In a further preferred embodiment, the hydromechanical linear converter according to the invention is characterized in that the valve body comprises a valve pot and a valve stem fixedly connected to it, whereby a bottom of the valve pot forms the valve head. The electromagnetic actuator acts on the valve stem. Preferably, a basket fixed to the housing protrudes into the valve pot, the spring unit being formed by a return spring surrounding the valve stem and supported on the basket. This ensures in a very compact manner that the return spring can act on the valve body via the valve stem and the valve body can thus be preloaded into a position corresponding to the first switching position of the valve unit.
Although the electromagnetic actuator in the context of the present invention can also be configured in other ways (e.g. as an electric linear motor), it is preferably configured as a solenoid unit for typical applications. For certain applications, it may be advantageous to dispose the solenoid (or the electromagnetic actuator designed in another way) in the hydraulic operating chamber, especially with regard to sealing. For typical applications, however, the advantages associated with disposing the solenoid unit (or other type of electromagnetic actuator) on the outside of the valve body outweigh the advantages associated with mounting the solenoid unit (or other type of electromagnetic actuator) on the outside of the valve body (including good mountability and accessibility of the electromagnetic actuator), even if this requires a moving part (e.g. an armature rod of the solenoid unit or the valve stem) to pass through the valve body (see below).
In the above sense, the solenoid unit preferably comprises an armature with an armature rod and an armature tube which receives (and possibly guides) the armature rod and is sealed tightly on one side. The armature of the linear solenoid unit preferably works “under oil”. The interior of the armature tube can communicate with the hydraulic operating chamber to ensure constant pressure compensation through the opening in the valve housing through which the armature rod, the valve stem or a separate tappet arranged between these components passes. This means that there is no need for dynamic sealing of the armature rod, the tappet or the valve stem, which allows for low friction and thus enables the use of a particularly efficient solenoid unit. However, the armature tube must be able to withstand high pressures (possibly by means of a housing supporting it), namely the maximum operating pressure in the hydraulic working chamber of the linear converter.
In the light of the latter aspect, the alternative is particularly advantageous where the valve stem, the armature rod or a separate tappet arranged between the valve stem and the armature rod is passed through the valve body at least in a substantially sealing manner and the interior of the armature tube communicates with the supply connection via a relief line. In this configuration, in order to avoid the friction associated with a 100% reliable seal between the valve stem/armature rod/tappet on the one hand and the valve housing on the other hand, a certain amount of slight oil leakage is permitted in the relevant passage towards the solenoid unit; however, the leakage oil in question does not build up any pressure in the armature tube, as it can flow off (unpressurised) through the relief line to the supply connection. This configuration places particularly low mechanical demands on the solenoid unit.
Another preferred further embodiment of the invention is that the valve seat is located between the fluid connection and the valve head. In this case—in the second switching position of the valve unit—the valve head rests against the valve seat on the side opposite the fluid connection. In this case, the surface portions of the valve body that are exposed to the pressure prevailing in the fluid connection in the second switching position of the valve unit and whose pressurization acts on the valve body in the same direction as the spring unit are primarily the surface of the valve head resting on the valve seat that is exposed to the fluid connection and enclosed by the valve seat. In this case, the compensation channel is preferably formed by an opening through the bottom of the valve pot. In this way, the hydraulic connection between the hydraulic working chamber and the hydraulic operating chamber can be established with very simple means, which has a positive effect on the manufacturing complexity as well as robustness and service life.
However, in functional reversal of the preferred configuration of the invention set out above, the valve seat may also be located between the supply connection and the valve head, so that the valve head—in the second switching position of the valve unit—abuts the valve seat on the side opposite the supply connection. This also represents a very advantageous configuration of the present invention. As those surface portions of the valve body which are exposed to the pressure prevailing in the fluid connection in the second switching position of the valve unit and whose pressurization acts on the valve body in the same direction as the spring unit, in this case primarily that portion of the end surface of the valve head is considered which surrounds the sealing surface acting together with the valve seat on the outside. Preferably, the compensation channel is formed by an opening through the side wall of the valve pot in this case.
Another preferred further embodiment of the inventive hydraulic linear converter is characterized in that the electromagnetic actuator is not energized in the first switching position. The valve body, as far as the above-mentioned hydraulic self-retaining mechanism is not effective, is moved by the spring unit into a position corresponding to the first switching position when the electromagnetic actuator is currentless, in which its valve head is lifted from the valve seat and the supply connection and the fluid connection are hydraulically connected.
According to another preferred further embodiment of the invention, the valve body can be brought into at least one intermediate position lying between the first and second switching position of the valve unit by means of the electromagnetic actuator. This enables the valve unit to assume an additional functionality, in particular as an effective flow throttle or fluid brake when the flow path between the fluid connection and the supply connection is only partially open when the valve body is brought into the intermediate position. This is the simplest way to achieve a stabilizing damping effect—which can be adjusted if necessary—in a suitable hydraulic environment. This allows a targeted influence on the pressure and flow conditions prevailing in the linear converter according to the invention with minimum effort; a substantial further improvement in the usability and extended applicability of the linear converter is the result.
Just to avoid misconceptions, it should be pointed out as a precautionary measure that the term “supply connection” must never be used to imply that the direction of flow through the valve unit from the supply connection to the fluid connection is mandatory. On the contrary, as already mentioned above, a reverse flow through the valve unit is also possible.
In the interest of increased flexibility of the inventive hydraulic linear converter, the hydraulic operating chamber communicates particularly preferentially with the supply connection of the valve unit via a bypass line with a shut-off valve arranged therein. In this way, the hydraulic operating chamber can be depressurized independently of the pressure conditions in the hydraulic working chamber, thus eliminating the hydraulic self-locking effect described above. This represents an additional safety functionality, because as a result the valve unit can be opened even under pressure in the hydraulic working chamber. As the hydraulic working chamber is connected to the hydraulic operating chamber through the compensation channel, the pressure in the hydraulic working chamber can also be reduced in a targeted manner—towards the supply connection—via the above-mentioned bypass line, even if the valve unit is (still) closed.
In the following, the present invention is explained in more detail by means of two preferred exemplary embodiments illustrated in the drawing. Thereby
The hydromechanical linear converter 1 illustrated in the drawing comprises, as known from the state of the art and therefore not explained in detail at this point, a cylinder 2, a piston unit 3 movable relative to it and a valve unit 4. The cylinder 2 and a piston 5 of the piston unit 3 define a hydraulic working chamber 6 into which a working connection 7 and a further fluid connection 8 open, the fluid connection communicating hydraulically with the valve unit 4. The valve unit 4 is configured as a seat valve unit 9 and comprises a supply connection 10 and can be switched between a first switching position connecting the supply connection 10 with the fluid connection 8 (shown in
The valve unit 4 comprises a valve housing 11, a valve body 12, a spring unit 13 and an electromagnetic actuator 14. The valve housing 11 comprises a pot-shaped insert 15 which forms the valve seat 16 and—in its peripheral wall—has several peripheral openings 17, and a two-part base body 18 with a base structure 19 having the supply connection 10 and the fluid connection 8 and a cover 20. Base structure 19 and cover 20 are firmly connected to each other with suitable (not shown) fastening means. They accommodate the insert 15 between them, whereby the insert 15 is sealed at the end face against the base structure 19 and the cover 20 by means of associated seals.
The valve body 12 can be moved along a valve axis A relative to the valve body 11. It comprises a valve pot 21—having a substantially cylindrical circumferential wall and a bottom—and a valve stem 22 which is firmly connected to the bottom of the valve pot 21, the bottom of the valve pot 21 forming the valve head 23 which cooperates with the valve seat 16. The valve seat 16 is located between the fluid connection 8 and the valve head 23. The spring unit 13 pretensions the valve body 12 to a position corresponding to the first switching position of the valve unit, in which the valve head 23 is lifted from the valve seat 16.
A compensation channel 24, configured as an opening 25, passes through the bottom of the valve pot 21, while the valve body 12 is sealingly guided in the valve housing 11—namely in its insert 15—in such a way that together with the latter it delimits a hydraulic operating chamber 26. In a projection along the valve axis A, the hydraulic operating chamber 26 is essentially limited by two surface portions of the valve pot 21, namely the surface of the bottom facing the interior of the valve pot (minus the surfaces of the opening 25 and the valve stem 22) and the annular end face of the circumferential wall. The sum of these surface portions, over which a force acting on the valve body 12 in the opposite direction to the operating direction of the spring unit 13 results when pressure is applied to the hydraulic operating chamber 26, is greater than the surface of the valve head 23 resting on the valve seat 16 being surrounded by the valve seat 16 and being exposed to the fluid connection 8. The hydraulic operating chamber 26 communicates hydraulically with the fluid connection 8 via the compensation channel 24, so that pressure compensation between the fluid connection 8 and the hydraulic operating chamber 26 is ensured.
A hydraulic connection between the hydraulic operating chamber 26 and the supply connection 10 can be established via a bypass line 27 with a shut-off valve 28, which is also electromagnetically operated.
A basket 29 fixed to the housing projects into the valve cup 21, on which is supported a helical return spring 30 surrounding the valve stem 22 and forming the spring unit 13. Its second end is supported by a collar of the valve stem 22.
The electromagnetic actuator 14 acts on the valve body 12 via a purely mechanical actuation chain. It moves the valve body 12 against the force of the spring unit 13 into a position corresponding to the second switching position of the valve unit, in which the valve head 23 rests sealingly on the valve seat 16.
The electromagnetic actuator 14 is configured as a solenoid unit 31, which comprises an armature with an armature stem 32 acting on the valve stem 22 and a pressure-tight armature tube which receives and guides the armature and is closed at one end. By means of an adapter 33 attached to the cover 20 of the valve housing, the solenoid unit 31 is firmly and tightly connected to the valve housing 11 in such a way that the interior of the armature tube is constantly exposed to the pressure prevailing in the hydraulic operating chamber 26. The corresponding constant pressure compensation takes place along the armature rod, which is guided with appropriate clearance.
Other configurations of the electromagnetic actuator (e.g. as an electric linear actuator) are advantageously possible in the same way (see above), in particular to enable the valve body to be adjusted to several different intermediate positions. From
The modified embodiment illustrated in
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2019 209 440.6 | Jun 2019 | DE | national |
