JP2016532042A - Transfer device for discharging fluid into a fluid conduit - Google Patents

Abstract

It has a transfer piston 27 which can be driven by the operating device 3 in the pump chamber 31, the transfer piston takes out the fluid from the fluid conduit 35 in a reduced direction in one transfer direction and the other, preferably the reverse In the transfer device, in which the valve device 39, 41 into the respective fluid conduit 35, 37 is a take-off process in which the pressure is reduced In the discharge process, each valve device 39, 41 opens in one fluid conduit 35, shuts off in the other fluid conduit 37, and vice versa. Are installed to act in the opposite direction so as to block in one fluid conduit 35 and open in the other fluid conduit 37. [Selection] Figure 1

Description

  The invention has a transfer piston that can be driven by an operating device in the pump chamber, the transfer piston taking out fluid in such a way as to reduce the pressure in the transfer direction from the fluid conduit, preferably in the opposite, other transfer direction The present invention relates to a transfer device that discharges fluid to another fluid conduit in such a manner that the pressure is increased.

  This type of transfer device is prior art and is used to transfer liquids isostatically in various fields. As a piston transfer pump operable by a lifting magnet, this type of transfer device is used in a variety of drive systems in which it is electrically controlled. In this type of application, high demands are placed on the driving behavior, in particular with regard to tolerances of the transfer pressure, quick response behavior with high repeatability and no hysteresis in periodic driving.

  In view of the above problems, it is an object of the present invention to provide a transfer device of the kind described above which is characterized by a particularly favorable driving behavior.

  This object is achieved according to the invention by a transfer device having the features of claim 1 in its entirety.

  According to it, the essential particularity of the present invention is that a valve device is installed in each fluid conduit associated with the pump chamber, and that valve device is one of the two in the take-off process to reduce the pressure. Opening in the transfer direction, blocking in the other transfer direction, and in the opposite case blocking in one transfer direction and opening in the other transfer direction. Thereby, high response accuracy and repeatability can be achieved without hysteresis.

  In the preferred embodiment, each valve device is formed from a check valve, the opening direction of which commonly points to a fluid transfer device defined in the associated fluid conduit.

  Particularly preferably, the arrangement is made such that each fluid conduit has one and the same conduit section with the same flow-through cross-section, calculated from the pump chamber to the corresponding check valve. ing. Thereby, a particularly high repeatability is achieved without hysteresis.

  Preferably, the free cross section of the pump chamber is then equal to or less than the free cross section of the conduit sections with respect to the connection area of the connected conduit sections. This uniform cross-sectional size is effective in terms of repeatability, particularly when the transfer flow is small and the transfer pressure is high.

  Particularly preferably, the arrangement can be made such that each fluid conduit is a component of a common fluid transfer lane into which a transfer piston built in the pump chamber is connected.

  The transfer piston has a needle-shaped protrusion in order to increase the repeatability in periodic drive and small transfer flow, in which case the needle-shaped protrusion is fitted into the pump chamber as an excluding body member, Each fluid conduit communicates into the free end of the pump chamber.

  Particularly preferably, the operating device is formed of an operating magnet which can be energized, and the operating magnet reduces the pressure of the transfer piston in the operating state without one current or in the other energized operating state. To a travel position that increases

  In a particularly preferred embodiment of the invention, a piston transfer pump comprising at least a transfer piston and a pump chamber has a maximum pressure in the pump chamber that can be predetermined if the pressure rises unintentionally in the fluid conduit. A pressure limiting device is provided to limit the pressure value. The pressure limiting device integrated into the pump chamber eliminates the need for other pressure limiting devices such as pressure limiting valves. Furthermore, the disadvantages that arise in attempts to limit pressure by using the stroke-force-characteristic curve of the magnetic operating device are avoided. In that case, the deviation of the electrical energy supply as specified is possible, which leads to drawbacks in response accuracy, hysteresis and repeatability.

  Particularly preferably, in order to form a pressure limiting device, the pumping chamber is adapted when a corresponding fluid pressure is generated in the fluid transfer lane, in particular in cooperation with a storage device in the form of a compression spring. It is possible to move into a return area that increases the capacity of the storage.

  In that case, in a particularly preferred embodiment, the arrangement acts permanently on the transfer piston, in particular with other energy storage devices in the form of other compression springs, which reduce the volume of the piston chamber with the transfer piston. It is made to try to move to the feed area. The pressure limit is thereby determined according to the characteristics of the two compression springs acting on the transfer piston, irrespective of the energy supply of the operating magnet.

  Hereinafter, the present invention will be described in detail using embodiments shown in the drawings.

FIG. 3 is a longitudinal sectional view schematically showing the embodiment of the transfer device according to the present invention in a greatly simplified manner. It is a longitudinal cross-sectional view which shows an Example, Comprising: The magnet housing of the electromagnetic operating device is removed, and the drive state of the operating magnet which is not energized is shown. FIG. 3 is a longitudinal sectional view corresponding to FIG. 2, showing a driving state of an energized operating magnet. FIG. 4 is a longitudinal sectional view corresponding to FIGS. 2 and 3, showing the drive state of the energized operating magnet with the pressure limit being active.

  In FIG. 1, a pump housing is denoted by reference numeral 1, and an operating magnet provided as an electrical operating device is denoted by reference numeral 3. The pump housing 1 has a hole 5, and an inner screw 7 is formed at the end of the hole located on the right side in FIG. 1. The operating magnet 3 is attached to the pump housing 1 by screwing the protruding portion 9 of the pole core 11 with the inner screw 7 of the hole 5. The operating magnet 3 has a coil winding 15 inside the magnet housing 13, and the coil winding surrounds the pole core 11 and the pole pipe 17 as is common in this type of operating magnet 3. The magnetic armature 19 is movable in the axial direction within the pole pipe, and the operation plunger 21 coaxial with the longitudinal axis of the hole 5 is firmly attached to the magnetic armature.

  A free end portion of the operation plunger 21 is in contact with the pressing body 23, and one end portion of the compression spring 25 is supported by the pressing body, and the other end portion of the compression spring is an operation of the pump transfer piston 17. The operation portion 26 of the pump transfer piston is guided so as to be able to travel in the axial direction in the hole 5. The transfer piston 27 has a needle-shaped protrusion 29 at the end opposite to the operation portion 26, and the protrusion fits into the pump chamber 31 as an original excluding part of the transfer piston 27, The pump chamber is formed as an overhang in the housing 1 with the diameter of the hole 5 being significantly reduced. The other compression spring 33 surrounding the transfer piston 27 between the operating part 26 and the step 28 formed in the hole 5 at the transition to the pump chamber 31 is operated with this step 28. It is mounted between the portions 26.

  As suggested by the symbolic representation in FIG. 1, a plurality of fluid conduits are associated with the pump chamber 31, and one of the first fluid conduits is indicated by reference numeral 35 and is being driven. The fluid is removed from the fluid conduit in such a way that the transfer piston 27 reduces the pressure. A fluid conduit is shown in FIG. 1 at 37 as it discharges fluid during drive as the transfer piston 27 increases pressure. A valve device is associated with the fluid conduits 35 and 37, and the valve devices are formed as check valves in the first fluid conduit 35 and the second fluid conduit 37, respectively. The check valve of the fluid conduit 35 is indicated at 39 and opens in a withdrawal process that reduces the pressure. A check valve, indicated at 41, in the second fluid conduit 37 opens in a discharge process that increases pressure. The fluid conduits 35, 37 are connected to a common transfer lane including the pump chamber 31, that is, a first conduit section 43 extending from the check valve 39 of the first fluid conduit 35 to the pump chamber 31 and a second from the pump chamber 31. A second conduit section 45 extending to the check valve 41 of the fluid conduit 37. The two conduit sections 43 and 45 have the same flow-through cross section and the same conduit length as a common transfer lane section.

  FIGS. 2 to 4, with the magnet housing 13 and winding 15 removed from the operating magnet 3, show more detailed details of the structural form of the piston transfer pump. In this case, FIG. 2 shows the drive state of the operating magnet 3 which is not energized, in which the armature 19 of the operating magnet 3 formed as a so-called pressing magnet has its terminal end located below in FIG. In position. The armature 19 takes this terminal position by the force applied from the energy storage device to the operation plunger 21 when there is no magnetic force. This energy storage device is formed by compression springs 33 and 25 as already described with reference to FIG. Among these compression springs, a compression spring 33 that surrounds the transfer piston 27 as a coil spring urges the transfer piston 27 in the traveling direction that increases the volume of the pump chamber 31, and the operation portion 26 of the transfer piston 27 is placed in the hole 5. Is held in contact with a slidable sleeve 47, which forms a kind of spring housing for the other compression spring 25. A restoring force applied from the compression spring 33 to the sleeve 47 and the other compression spring 25 is applied to the plunger 21 and the magnetic armature 19 along with the pressing body 23. In the drive state where current is not supplied, the needle-shaped protrusion 29 of the transfer piston 27 is at a position where the pump chamber 31 has its maximum volume, as shown in FIG.

  FIG. 3 shows a driving state when the operating magnet 3 is energized, in which case the magnetic armature 19 has moved from its end position (upward in FIG. 3). This sliding movement that the plunger 21 transmits to the pressing body 23 acts on the sleeve 47 and the operation portion 26 of the transfer piston 27 through the compression spring 25 that contacts the pressing body 23. The transfer piston is moved to the end position shown in FIG. 3 by the sliding force applied through the compression spring 25, and the transfer piston 27 is moved to the end position adjoining the shoulder 28 at the end position, and is excluded at the end position. Projections 29 used as body parts push fluid out of the pump chamber 31 into the conduit sections 43, 45 (in this piston position the pump chamber 31 itself is no longer visible in FIG. Becomes). This traveling movement of the transfer piston 27 is performed against the spring force of the compression spring 33.

  FIG. 4 shows the driving state in which the operating magnet 3 is energized again, so that the magnetic armature 19 is moved from the retracted end position (upward in FIG. 4). However, unlike in FIG. 3, despite the fact that the magnetic piston 19 has moved from its end position, the transfer piston 27 is not in its end position, which completely eliminates the volume of the pump chamber 31, and the pump chamber It has returned to the position which removes a pressure load by the transfer force which actually acts on the connection locations 43 and 45 of 31. This compensation movement, which prevents the transfer pressure from exceeding the target value, has exceeded the action of the other compression springs 25 when the pressing force acting on the protrusion 29 in the pump chamber 31 is combined with the spring force of the compression springs 33. Sometimes it starts. In other words, the pressure threshold value at which the backward movement that limits the pressure of the transfer piston 27 is started can be adjusted by the spring characteristics of the compression springs 33 and 25. Therefore, since the pressure limit is mechanically determined and depends on the magnetic force of the operating device, a pressure-stable transfer with high periodic repeatability and without hysteresis can be achieved.

Claims (10)

It has a transfer piston (27) which can be driven by an operating device (3) in the pump chamber (31), said transfer piston taking out fluid from the fluid conduit (35) in such a way as to reduce the pressure in one transfer direction. And in another, preferably the opposite, transfer device that discharges the fluid into the other fluid conduit (37) in a transfer direction in a pressure-enhancing manner,
Valve devices (39, 41) into the respective fluid conduits (35, 37) are opened in one fluid conduit (35) in the case of an extraction process that reduces the pressure. In a discharge process that shuts off in the other fluid conduit (37) and vice versa, each valve device (39, 41) shuts off in one fluid conduit (35), A transfer device characterized in that it is mounted to act in the opposite direction so as to open in the fluid conduit (37).   Each valve device is formed by a check valve (39, 41), and the opening direction of the check valve is a common, fluid transfer direction defined in the associated fluid conduit (35, 37). The transfer device according to claim 1, wherein   One and the same conduit section with the same flow-through cross section, each fluid conduit (35, 37) being calculated from the pump chamber (31) to the associated check valve (39, 41), respectively The transfer apparatus according to claim 1, wherein the transfer apparatus has (43, 45).   Characterized in that the free cross section of the pump chamber (31) is less than or equal to the free cross section of these conduit sections with respect to the connection region of the connected conduit sections (43, 45), respectively. The transfer device according to any one of claims 1 to 3.   Each fluid conduit (35, 37, 43, 45) is a component of a common fluid transfer lane (43, 45), in which a transfer piston (31) containing a pump chamber (31) is built. The transfer device according to any one of claims 1 to 4, wherein 27) is connected.   A needle-shaped protrusion (29) of the transfer piston is fitted into the pump chamber (31), and each fluid conduit (43, 45) communicates with the free end of the pump chamber. The transfer apparatus of any one of Claims 1-5.   The operating device is formed of an operating magnet (3) that can be energized, and the operating magnet reduces the pressure of the transfer piston (27) in one operating state without current or the other energized operating state. Alternatively, the transfer device according to claim 1, wherein the transfer device is moved to a traveling position where pressure is increased.   When the pressure rises unintentionally in the fluid transfer lanes (43, 45) to the piston transfer pump consisting of at least the transfer piston (27) and the pump chamber (31), the pressure inside the pump chamber (31) 8. Transfer device according to any one of the preceding claims, characterized in that a pressure limiting device (33) is provided so as to be limited to a maximum pressure value that can be determined.   In order to form a pressure limiting device, the transfer piston (27) cooperates with an energy storage device, in particular in the form of a compression spring (33), to generate a certain fluid pressure in the fluid transfer lanes (43, 45). The transfer device according to any one of claims 1 to 8, wherein the transfer device is movable into a return region that increases the capacity of the pump chamber (31).   The transfer piston (27) is permanently acted upon, in particular by another energy storage device in the form of another compression spring (25), which reduces the transfer piston (27) and the volume of the pump chamber (31). The transfer device according to any one of claims 1 to 9, wherein the transfer device is intended to be moved to a feed region.

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