JP2010230010A - Device for adjusting volume and discharging lubricant agent - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve a device for adjusting a volume and discharging a lubricant agent. <P>SOLUTION: The device is provided with a base system equipped with a connecting section for a track of the lubricant agent, a control piston positioned in the base system in a movable manner and equipped with a control element, and a lubricant piston positioned in the base system in a movable manner and equipped with a volume adjusting chamber. The control piston, the lubricant piston, and the base system form a pressure chamber with a volume that is variable according to the motion of the control piston and/or the lubricant piston. The control piston and/or the lubricant piston are movable in the base system by a pressure load of the pressure chamber. Both the pistons are formed in such a way that the volume adjusting chamber can be connected to a lubricant agent exit of the base system by the control element by the motion of the control piston in the base system. When the volume adjusting chamber is connected to the lubricant agent exit, the lubricant piston becomes movable in the base system so that the lubricant agent in the volume adjusting chamber can be supplied to the lubricant agent exit. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an apparatus for metering out a lubricant.

  This type of device is used, for example, to lubricate cylinders in large diesel engines, such as large diesel engines such as those used in ships. In CH6733506A5, an apparatus for lubricating a cylinder of a reciprocating internal combustion engine is known. The cylinder to be lubricated is provided with a plurality of lubricant tubes distributed around the cylinder and open to the respective cylinder running surfaces. A piston-cylinder system is connected to each of these lubricant tubes. The piston-cylinder system allows the lubricant to be drawn in via the suction valve and pumped to the corresponding lubricant tube via the discharge valve. In order to dispense the lubricant, each provided piston-cylinder system can be loaded with a hydraulic pressure medium. A compression spring located in the piston-cylinder system provides a corresponding return force for each lubricant discharge stroke. As a result, the cylinder can subsequently carry out a new work step for distributing the lubricant again by means of the pressure medium.

  In DE 19743955 B4, a comparable cylinder lubrication device for a multi-cylinder internal combustion engine is described. However, in this known cylinder lubricating device, at the same time, the lubricant to be dispensed for lubrication is introduced into the dispensing device under pressure and used to move the metering piston. Also in this known cylinder lubrication device, the return of the metering piston is performed by a return spring arranged in the device.

CH6733506A5 DE19743955B4

  The object of the present invention is to provide an improved device for metering and releasing lubricant.

  In order to solve the above problems, in the configuration of the present invention, at least one control comprising a base system comprising a connection for a line of lubricant and at least one control element movably disposed in the base system. A piston, and at least one lubrication piston with at least one metering chamber movably disposed within the base system, the control piston, the lubrication piston and the base system comprising the control piston and / or Or at least one pressure chamber having a variable volume by movement of the lubrication piston, wherein the control piston and / or the lubrication piston is movable in the base system by a pressure load of the pressure chamber; And the lubrication piston of the control piston in the base system. The metering chamber of the lubrication piston is configured to be connectable to the lubricant outlet of the base system by the control element by movement, and when the metering chamber is connected to the lubricant outlet, The piston was movable in the base system so that the lubricant in the metering chamber was supplied to the lubricant outlet.

  An advantageous configuration is the invention according to the dependent claims.

  Preferably, the lubrication piston is formed in a substantially annular shape, and the control piston is disposed in the lubrication piston.

  Preferably, the control element of the control piston is configured as a groove.

  Preferably, the control piston includes at least one metering hole, and each of the pressure chambers can be connected to at least one of the metering chambers through the metering hole.

  Preferably, a valve is disposed in the metering hole, and the valve is formed so that the lubricant can be supplied from the pressure chamber into the metering chamber and the backflow of the lubricant is prevented. ing.

  Preferably, at least one metering chamber in the lubricating piston is formed by at least one hole, in which a pumping piston coupled to the base system is arranged, the pumping piston being When the metering chamber is connected to the lubricant outlet and the lubricating piston moves toward the pumping piston, the volume of the metering chamber is reduced and the lubricant present in the metering chamber is The lubricant is supplied to the outlet.

  Preferably, when the lubrication piston moves away from the pumping piston, the volume of the metering chamber can be expanded, and the lubrication piston and the control piston are configured so that the metering chamber has the pressure through the metering hole. The metering chamber is arranged to be filled with a lubricant during volume expansion. Preferably, two pressure chambers facing each other with respect to the control piston are provided, and each pressure chamber is provided with at least one of the metering hole and at least one of the metering chamber and the pressure feeding piston. Has been. Preferably, an input connection provided in the base system capable of supplying lubricant to the base system under pressure, and provided in the base system capable of supplying lubricant to the reservoir without pressure. A return connection portion, and a directional control valve capable of alternately connecting the input connection portion and the return connection portion to each of the pressure chambers.

  Preferably, at least two pressure chambers and at least two metering chambers and at least two corresponding metering holes are provided, the pressure chambers being alternately under pressure by appropriate control of the directional control valve The control piston and the lubrication piston can be loaded with a lubricant, and each time the pressure load is switched, the following method steps are performed: the control piston is pressureless each time by the pressure in the corresponding pressure chamber. When moving toward the pressure chamber and reaching the end stopper, the metering chamber of the lubricating piston disposed in the pressureless pressure chamber is connected to the lubricant outlet by the corresponding control element. The lubricating piston is moved toward the pressureless pressure chamber by the pressure in the corresponding pressure chamber, and the pressureless pressure is moved by the movement. The metering chamber disposed in the chamber is reduced based on the pumping piston, and the contained lubricant is supplied to the lubricant outlet via the control element, and at the same time, lubrication is performed by the motion of the lubricating piston. The volume of the metering chamber of the piston disposed in the pressure chamber to be pressure-loaded is enlarged based on the pressure-feeding piston and connected to the pressure chamber to be pressure-loaded by a corresponding metering hole. Thus, the method step of filling the expanding volume of the metering chamber with a lubricant is carried out.

  Preferably, the lubricating piston has an axially extending notch disposed in the center, and the control piston is disposed in the notch.

  Preferably, the notch and the accommodated control piston are formed so as to prevent the control piston from rotating around the axial direction.

  Preferably, a sensor capable of monitoring movements of the control piston and the lubrication piston is provided.

  Preferably, the base system comprises a central unit for housing the lubrication piston and the control piston, on which the line for the lubricant is arranged, and on the end side for forming the pressure chamber Two end pieces arranged in a central unit, and a pumping piston arranged in the end piece so as to engage in a corresponding hole of the lubricating piston to form the metering chamber.

An apparatus for metering and releasing a lubricant according to the present invention comprises:
-A base system with connections for the lines of lubricant;
-At least one control piston comprising at least one control element movably arranged in the base system;
-At least one lubricating piston comprising at least one metering chamber, which is movably arranged in the base system;
With
The control piston, the lubrication piston and the base system form at least one pressure chamber with a variable volume by movement of the control piston and / or the lubrication piston;
The control piston and / or the lubrication piston are movable in the base system by the pressure load of the pressure chamber;
The control piston and the lubrication piston are formed in such a way that the metering chamber of the lubrication piston can be connected to the lubricant outlet of the base system by the control element by the movement of the control piston in the base system; And
-When the metering chamber is connected to the lubricant outlet, the lubrication piston is movable in the base system so that the lubricant of the metering chamber is supplied to the lubricant outlet; Features.

  The device formed as described above is clearly simple in terms of mechanical components compared to known systems, and thus can be configured compactly and can be manufactured inexpensively. The control piston and the lubrication piston are formed so that the metering chamber of the lubrication piston is connected to the lubricant outlet of the base system by the control element by the movement of the control piston, so that the lubricant outlet due to the pressure load of the pressure chamber The supply of lubricant in is easily guaranteed. Unless the lubrication piston metering chamber is connected to the lubricant outlet of the base system, no lubrication piston movement occurs. The volume of the metering chamber is kept constant even under pressure unless a connection to the lubricant outlet is established by the contained lubricant. Thus, no lubricant is provided at the lubricant outlet until a connection to the lubricant outlet occurs. Only after the control piston has been moved by the pressure load and has achieved a predetermined position, for example, is the metering chamber connected to the lubricant outlet of the base system by means of a control element. Only this connection allows the movement of the lubrication piston, so that the lubricant is moved from the metering chamber to the lubricant outlet based on the movement of the lubrication piston caused by the pressure in the pressure chamber and the corresponding connection. Guided. Advantageously, the movement of the lubricating piston is also performed on the basis of the pressure load of the pressure chamber. Again, advantageously, the pressure loading of the pressure chamber is effected by the lubricant itself. Thus, the lubricant is not only present in the metering chamber of the lubrication piston, but is also supplied to the pressure chamber under pressure. Thus, a separate line system for the hydraulic medium for pressure chamber pressure loading and piston control is not required. This additionally simplifies the device compared to known lubrication devices.

  In an advantageous form of the invention, the lubrication piston is formed in a substantially annular shape and the control piston is arranged in the lubrication piston. In this way, a particularly compact form of the device is possible.

  In an advantageous embodiment of the device, the control element of the control piston is configured as a groove. This allows a simple connection of the metering chamber with the lubricant outlet of the base system at the appropriate position and arrangement of the metering chamber in the groove and the lubricating piston. Particularly when the control piston is arranged in the lubricating piston, this embodiment has the advantage that the connection between the metering chamber and the lubricant outlet can be easily formed via a groove. The lubricating piston is preferably connected on the one hand to the lubricant outlet of the base system and on the other hand via a control element, preferably a control element in the form of a groove, which is also arranged in the lubricating piston. It has a hole that can be connected to the mass chamber. At a predetermined position of the control piston, the metering chamber is connected to the lubricant outlet of the base system by a groove and a hole. As a result, the lubricating piston can move as described above and provide lubricant to the lubricant outlet of the base system.

  In an advantageous form of the invention, the control piston comprises at least one metering hole, through which each of the pressure chambers can be connected to at least one of the metering chambers. Lubricant under pressure can be supplied from the pressure chambers to the respective metering chambers through the metering holes at predetermined positions of the control piston and the lubricating piston. This allows the lubricant to be prepared in the metering chamber for the next lubrication cycle. Thereby, for example, in an apparatus including two pressure chambers facing each other and at least two corresponding metering chambers arranged in one pressure chamber, the lubricant is applied on the pressure-loaded side. At the same time that the metering chamber is replenished, on the opposite side, it is possible to provide lubricant to the lubricant outlet from the metering chamber arranged in the pressure chamber that is not pressure-loaded. If the pressure load is reversed accordingly, the same cycle is performed in the other direction. As a result, the metering chamber filled with the lubricant in the previous cycle is located on the pressure chamber side switched to no pressure, so that the control piston and the lubrication piston are operated during the corresponding movement and through the control element. When the metering chamber is connected to the lubricant outlet, the metering chamber lubricant is correspondingly provided. In that respect, lubricant can be provided to the lubricant outlet at every pump cycle, and in the meantime, the corresponding metering piston is returned by a spring to allow new lubricant to be delivered, as in known devices. There is no need to accept and be able to provide the lubricant outlet.

  In an advantageous embodiment of the invention, at least one metering chamber in the lubricating piston is formed by at least one hole, in which a pumping piston fixedly connected to the base system is arranged. The pressure-feeding piston is configured such that when the metering chamber is connected to the lubricant outlet and the lubricating piston moves relative to the pressure-feeding piston, the volume of the metering chamber is reduced, The lubricant existing in the metering chamber is supplied to the lubricant outlet. This additionally ensures that the lubrication piston is stationary even when the pressure chamber is under pressure unless the pressure chamber is connected to the lubricant outlet. That is, when the lubricant is present in the metering chamber, the lubricant cannot be discharged from the metering chamber, so that the volume of the metering chamber is not reduced by the movement of the lubricating piston. Therefore, with this configuration of the metering chamber having the pressure feed piston in the lubricating piston, when the pressure chamber is simply loaded with pressure, the control piston is first connected to the metering chamber with the lubricant outlet. It is guaranteed to move until formed by the control elements. The pressure in the pressure chamber then moves the lubrication piston and automatically reduces the volume of the metering chamber based on the stationary arrangement of the pumping piston, and correspondingly lubricates, preferably the control piston. The control element is guided to the lubricant outlet by the groove-like shape of the control element. As soon as the lubricating piston reaches the end stop in the base system, the release of lubricant at the lubricant outlet ends. At the same time, a minimum volume of the metering chamber is achieved.

  In an advantageous form of the invention, the volume of the metering chamber can be expanded when the lubrication piston moves away from the pumping piston, and the metering chamber has the metering hole in the lubrication piston and the control piston. The metering chamber is arranged so as to be filled with a lubricant during volume expansion. Thereby, the volume of the metering chamber is again expanded by a simple movement of the lubrication piston, and at the same time the lubricant is received from the pressure chamber connected to the metering hole by a suitable arrangement of the metering holes in the control piston. . Thereafter, again, the lubricant is prepared in the metering chamber for the next release at the lubricant outlet, so that the next work cycle for this metering chamber can be started.

  In a particularly advantageous form of the invention, two pressure chambers are provided opposite to each other with respect to the control piston, each pressure chamber having at least one of the metering holes and the metering chamber and the pressure feed piston, respectively. At least one of the above is disposed. Thus, when the control piston is appropriately configured, one of the metering chambers is connected to the lubricant outlet by the control element in each working stroke, and the lubricant is supplied from the metering chamber to the lubricant outlet. At the same time, on the pressure-loaded side, the corresponding volume of the corresponding metering chamber is enlarged by the movement of the lubricating piston and filled with the lubricant from the pressure-loaded pressure chamber. Therefore, the pressure load is correspondingly reversed, the direction of movement of the control piston is accordingly reversed first, and the newly filled metering chamber on the non-pressure-loaded side of the base system is accordingly connected to the lubricant outlet accordingly. Therefore, during the subsequent movement of the lubrication piston, the lubricant is supplied from the metering chamber to the lubricant outlet on the non-pressure side, and at the same time provided on the control piston on the pressure load side of the base system. Through the corresponding metering hole, the lubricant is supplied to the volume of the metering chamber which expands as the lubricating piston moves. This achieves two lubricant dispenses at the lubricant outlet in one complete work cycle of the device. Thereby, alternately filling one metering chamber and releasing the lubricant from the other metering chamber are performed simultaneously.

Advantageously, the device according to the invention comprises:
An input connection provided in the base system capable of supplying lubricant to the base system under pressure;
-A return connection provided in the base system capable of supplying lubricant to the reservoir without pressure;
A directional control valve capable of alternately connecting the input connecting portion and the return connecting portion to each of the metering chambers;

  This simply ensures that one of the pressure chambers can always be pressure loaded and the other is pressureless. Appropriate movement of these components from a pressure-loaded pressure chamber to a pressure-free pressure chamber is assured by the appropriate configuration of the control piston and the lubricating piston. Since the pressure load is reversed by an appropriate operation of the direction control valve, the pressure chamber that was not previously pressure-loaded is now pressure-loaded. Thereby, the movement of the control piston and the subsequent movement of the lubrication piston is reversed compared to the previous cycle. Thereby, simply, the double action of the device according to the invention is preferably achieved.

In an advantageous embodiment of the device according to the invention, at least two pressure chambers, at least two metering chambers and at least two corresponding metering holes are provided, the pressure chambers being controlled appropriately by the directional control valve. Can be alternately loaded with a lubricant under pressure, and the control piston and the lubrication piston each time the pressure load is switched:
-The control piston is moved by the pressure in the corresponding pressure chamber each time towards the pressureless chamber;
-When reaching the end stopper, by connecting the metering chamber of the lubrication piston arranged in the pressureless chamber to the lubricant outlet by the corresponding control element,
The lubricating piston is moved towards the non-pressure chamber by the pressure in the corresponding pressure chamber;
-By this movement, the metering chamber arranged in the non-pressure chamber is reduced based on the pumping piston, and the contained lubricant is supplied to the lubricant outlet via the control element;
-Simultaneously, due to the movement of the lubricating piston, the volume of the metering chamber of the lubricating piston arranged in the pressure chamber to which pressure is applied is expanded on the basis of the pumping piston and by the corresponding metering hole Connecting to the pressure chamber to which pressure is applied, and filling the expanding volume of the metering chamber with a lubricant,
The method steps are configured to be performed.

  A particularly compact and efficient working device is thus provided. In each complete work cycle, at least one of the metering chambers is filled with lubricant, and lubricant is supplied to the lubricant outlet from the opposing metering chamber. In the second or second half of the cycle, on the contrary, the lubricant is supplied to the lubricant outlet from the metering chamber filled in the first or first half, and is emptied in the first or first half of the cycle. The metering chamber is refilled with filler. Thus, a device that has been worked and formed in this manner has no wasted time during which no lubricant can be provided.

  Other advantages and forms can be seen from the embodiments described below with reference to the accompanying drawings.

1 is a sectional view of an advantageous embodiment of the invention in a first operating state; FIG. It is a figure which shows embodiment shown in FIG. 1 in the 2nd driving | running state. It is a figure which shows embodiment shown in FIG. 1 in the 3rd driving | running state. FIG. 2 is an alternative cross-sectional view of the embodiment shown in FIG. FIG. 2 is a schematic circuit diagram of the embodiment shown in FIG. 1. It is the figure which looked at the external appearance of embodiment shown in FIG. 1 from various directions. It is the figure which looked at the external appearance of embodiment shown in FIG. 1 from various directions. It is the figure which looked at the external appearance of embodiment shown in FIG. 1 from various directions. It is the figure seen in the same direction as FIG. 6 of the assembled state. It is the figure seen in the same direction as FIG. 7 of the assembled state. It is the figure seen in the same direction as FIG. 8 of the assembled state.

  FIG. 1 is a sectional view of a lubricant pump 1 as an embodiment of the present invention. The lubricant pump 1 includes a housing 3. The housing 3 includes hollow chambers 4a and 4b inside. The housing 3 including the pressure chambers 4a and 4b is closed at the end by a cap 5a or 5b. An annular seal ring 7 is provided between the housing 3 and the end cap 5a or 5b. Thereby, the pressure chambers 4 a and 4 b formed in the housing 3 are sealed from the outside by the seal ring 7. The housing 3 has two connections 9 or 11 for the lubricant on the upper surface. From the connecting parts 9 and 11, one lubricant passage 13 or 15, which extends in the radial direction, extends through the housing 3. On the lower surface of the housing 3, the lubricant passage 13 is connected to the lubricant outlet 17, and the lubricant passage 15 is connected to the lubricant outlet 19. A controllable directional control valve 21 is attached to the housing 3 in the region of the lubricant connections 17 and 19 below the housing 3. By means of the directional control valve 21, the lubricant connection parts 17 and 19 are selectively connected to a lubricant passage 23 or 25 which is also formed in the lower surface of the housing 3. The lubricant passage 23 or 25 extends in the lower part of the housing 3 and terminates in the pressure chamber 4a or 4b at the opposite end of the housing 3 in the vicinity of the respective seals 7 respectively. Accordingly, each of the lubricant connecting portions 9 or 11 is connected to the pressure chamber 4a or 4b via the respective passage 13 or 15, the lubricant connecting portion 17 or 19, the direction control valve 21, and the respective passage 23 or 25. Connectable.

  A lubricating piston 27 is disposed in the housing 3. The lubrication piston 27 is kept shorter than the housing 3 with respect to the extending length in the axial direction. As a result, the lubricating piston 27 can reciprocate between the pressure chambers 4a and 4b in the axial direction. The lubricating piston 27 has two opposed, bent or T-shaped holes on the upper and lower sides, respectively. These holes function as metering chambers 29a, 29b, 29c and 29d. In addition, the lubrication piston 27 comprises two central passages 31a and 31b extending in the radial direction.

  The housing 3 includes a lubricant outlet 33 that communicates with the passage 31 a of the lubricating piston 27. Since this passage 31a is configured to be expanded on the upper side, it always communicates with the lubricant outlet 33 regardless of the position of the lubricating piston 27 between the pressure chambers 4a and 4b. The passage 31b of the lubrication piston 27 is connected to another lubricant outlet in the housing 3 following another corresponding path not shown in FIG. Since this passage 31b also has an extended portion, it is connected to the corresponding lubricant outlet regardless of its position.

  Opposing pumping pistons 35 are disposed on each of the end caps 5a or 5b. The pumping piston 35 is clamped between the housing 3 and the respective end caps 5a and 5b by a fixed disk 37, respectively. The pressure-feeding pistons 35 are arranged so as to enter one of the passages of the lubricating piston 27 in the axial direction to define the metering chambers 29a to 29d. When the lubricating piston 27 reciprocates within the housing 3, the volumes of the metering chambers 29a to 29d change. In the drawing selected in FIG. 1, the lubricating piston 27 is positioned in contact with the stopper on the left side of the housing 3, so that it is in contact with the corresponding fixed disk 37. As a result, the volumes of the metering chambers 29a and 29c are minimal. At the same time, since the lubricating piston 27 is located farthest from the end cap 5b, the volumes of the metering chambers 29b and 29d are maximum. When the lubricating piston 27 moves toward the end cap 5a, the volumes of the metering chambers 29b and 29d are continuously reduced, and the volumes of the metering chambers 29a and 29c are increased at the same rate.

  The lubrication piston 27 includes a hole disposed in the center. A control piston 39 is disposed in the hole. The control piston 39 is formed longer than the lubrication piston 27 with respect to the extending length in the axial direction. A cutout is provided in each of the end caps 5a and 5b at a certain height. A control piston 39 can be engaged with each notch. The control piston 39 can also reciprocate between the pressure chambers 4a and 4b.

  The control piston 39 includes two control grooves 41a and 41b. The control grooves 41a and 41b extend on the outer surface of the control piston 39 partially along the control piston 39 in the axial direction. The control grooves 41a and 41b are extended and arranged so that the metering chamber 29a is connected to the passage 31 of the lubricating piston 27 when the control piston 39 is in the illustrated position. Similarly, the metering chamber 29c is also connected to the passage 31b via the control groove 41b.

  Further, the control piston 39 is formed in a T shape, and includes two passages 43 a and 43 b disposed at the axial ends of the control piston 39. The passages 43a and 43b are arranged so that the pressure chamber 4b is connected to the metering chambers 29b and 29d via the passage 43b at the illustrated position of the control piston 39, respectively. One valve 45 is disposed in each of the passages 43a and 43b. With the respective valves 45, the lubricant can only flow into the metering chambers 29 b and 29 d from the pressure chamber 4 b through the passage 43 b, but cannot flow out from the metering chambers 29 b and 29 d to the pressure chamber 4 in the reverse direction. It is guaranteed. The valve 45 includes a spring. This spring presses the closure cap towards the respective pressure chamber 4a or 4b, so that the passage 43a or 43b is closed in the basic state. Each closure cap is geometrically formed to abut against a corresponding step provided in the passage 43a or 43b to seal it.

  By disposing the control piston 39 and the lubricating piston 27 in the center, the pressure chambers 4a and 4b existing in the housing 3 are separated in the axial direction. As a result, no liquid is exchanged between the pressure chambers 4a and 4b even when pressure is applied. Depending on the position of the control piston 39 and the lubrication piston 27, the volume of one of the pressure chambers 4a or 4b is maximum and the corresponding volume of the other is minimum. In the position shown in FIG. 1 of the control piston 39 and the lubricating piston 27, the pressure chamber 4b has the maximum volume, while the pressure chamber 4a has only the minimum volume.

  Each of the end caps 5a or 5b has an air bleeding unit 47 on the upper side. The air vent unit 47 is connected to the pressure chamber 4a or 4b through a planar notch provided in the end cap 5a or 5b. As a result, the pressure chamber 4a or 4b is vented.

  FIG. 2 shows the lubricating pump 1 of FIG. 1 in another operating state. In this operating state, the control piston 39 is in a position different from that in FIG. The control piston 39 is disposed in contact with the right end stopper. As a result, the volume of the pressure chamber 4b is reduced, and the volume of the pressure chamber 4a is increased. However, since the lubricating piston 27 is still in the same position as in FIG. 1, the volume relationship is not completely the opposite of that shown in FIG. Based on the movement of the control piston 39, the metering chamber 29b is now connected to the passage 31a via the control groove 41a. Similarly, the metering chamber 29d is also connected to the passage 31b via the control groove 41b. Based on the fact that the passage 31a or 31b is connected to the lubricant outlet 33 respectively, the lubricant present in the metering chambers 29b and 29d is transferred to the lubricant outlet 33 via the passages 41a and 41b and 31a and 31b. Can be provided. However, the lubricating piston 27 is still in a position in contact with the stopper on the left side of the housing 3. As soon as the lubricating piston 27 moves to the right, the respective volumes of the metering chambers 29b and 29d are reduced based on the stationary arrangement of the pumping piston 35, and the lubricant passes through the passages 43a and 43b and 31a and 31b. Supplyed to the lubricant outlet 33. The lubrication piston 27 can move only when the metering chamber 29b or 29d is connected to the passage 41a or 41b. The control grooves 41a and 41b are dimensioned with respect to the axial extension length so that the metering chamber 29b is connected to the passage 31a via the control groove 41a during the entire movement of the lubricating piston 27. The passage 31 a is connected to the lubricant outlet 33 during the entire movement of the lubricating piston 27 based on the fact that the passage 31 a is configured to be expanded on the upper side. Therefore, the lubricant is evenly discharged from the lubricant outlet 33 during the movement of the lubricating piston 27.

  FIG. 3 shows the end state of the work cycle of the lubricant pump 1. This end state is achieved when the lubricating piston 27 also contacts the right end stopper, that is, the fixed disk 37. At this position, the volumes of the metering chambers 29b and 29d are minimum, and the discharge of the lubricant at the lubricant outlet 33 is completed. At the same time, by the movement of the lubricating piston 27, the metering chambers 29a and 29c are connected to the pressure chamber 4a via the passage 43a. Compared with the positions shown in FIGS. 1 and 2, the volumes of the metering chambers 29a and 29c are the maximum. Therefore, the lubricant flows from the pressure chamber 4a into the metering chambers 29a and 29c through the passage 43a and the valve 45. The pressure governing the inside of the pressure chamber 4a compresses the spring of the valve 45, and the closing cap is removed from the closed position.

  The lubricant pump 1 is in the opposite state in FIG. 3 as compared to the depiction in FIG. In this state, the volume of the pressure chamber 4a is expanded to the maximum, and the metering chambers 29a and 29c are filled with the lubricant. From this state, when the control piston 39 moves toward the end cap 5a, the metering chamber 29a is connected to the passage 31a via the control groove 41a. Subsequently, the lubricating piston 27 can move. Accordingly, the lubricant is supplied from the metering chamber 29a to the lubricant outlet 33 through the control groove 41a and the passage 31a. At the same time, during this oppositely directed movement, the metering chambers 29b and 29d are again filled with lubricant by connection with the pressure chamber 4b via the passage 43b. As a result, after the completion of the complete work cycle, the initial state shown in FIG. 1 is achieved again. Therefore, the lubricant is supplied to the lubricant outlet 33 twice during one work cycle of the lubricant pump 1. At the same time, one pair of metering chambers 29a to 29d is filled with lubricant, and the lubricant is discharged from the other pair. Thus, the lubricant pump 1 does not have the waste time that has to re-create the original position of the piston using a return spring, for example as known in the prior art.

  The movements of the control piston 39 and the lubrication piston 27 are caused by one pressure chamber 4a or 4b passing through the passage 23 or 25, the direction control valve 21, the passage 17 or 19 and the passage 9 or 11, respectively. Done by connecting to. For example, in one embodiment, the connecting portion 9 is loaded with a lubricant under pressure. In the initial state of the lubricant pump 1 shown in FIG. 1, the pressure chamber 4 a having the smallest volume is connected to the lubricant connection portion 9 via the direction control valve 21. As a result, the lubricant flows into the pressure chamber 4a under pressure. The pressure chamber 4b is simultaneously connected to the connection portion 11 via the direction control valve 21 and the corresponding passage. The connecting part 11 is connected to a reservoir for lubricant without pressure. Based on the pressure difference between the pressure chambers 4a and 4b, the control piston 29 moves from the position on the left side toward the end cap 5b. As soon as the control piston 39 reaches the position shown in FIG. 2, ie the right end stopper, the metering chambers 29b and 29d are connected to the respective lubricant outlets 33 via the control grooves 41a and 41b. The movement of the lubricating piston 27 caused by pressure is also possible. Based on the movement of the lubricating piston 27, the original lubricant discharge is performed as described above. As soon as the lubricating piston 27 reaches the final position shown in FIG. 3, the pressure load of the pressure chambers 4 a and 4 b is switched via the direction control valve 21. As a result, the pressure chamber 4b is now connected to the connecting portion 9 and connected to the lubricant under pressure. At the same time, the pressure chamber 4a is connected to the connecting portion 11 and connected to the reservoir without pressure. As a result, the movements of the control piston 39 and the lubrication piston 27 can be carried out in the reverse direction in turn. As soon as the position shown in FIG. 1 is reached again, the pressure loads in the pressure chambers 4a and 4b are switched again. Thus, the pump operation is simply maintained by the periodic control of the direction control valve 21, and the lubricant is discharged from the lubricant outlet 33 twice for each complete work process without interrupting the discharge of the lubricant during that time. To be prepared.

  The lubrication piston 27 and the pressure-feed piston 35 have end surfaces having different sizes based on different sizes at their axial ends. This increases the pressure ratio between the lubricant input pressure and the pressure provided at the lubricant outlet 33. Thus, a high pressure can be achieved at the lubricant outlet 33 even with a relatively small input pressure.

  By assembling different fixed disks 37, the amount of lubricant provided at the lubricant outlet 33 is changed. Thus, if the thin fixed disk 37 is used, the volume of the metering chambers 29a to 29d is increased, so that more lubricant can be pumped in each work process. On the other hand, if a thick fixed disk 37 is used, the volume of the metering chambers 29a-29d is reduced and correspondingly less lubricant is pumped.

  FIG. 4 shows the embodiment shown in FIGS. 1 to 3 in a cross-sectional view in the plane of one fixed disk 37. The housing 3 has a square outer surface. The axially extending holes 71 are symmetrically arranged at the housing edge and serve to fix the end caps 5 a and 5 b to the housing 3. In the partial region 73 of FIG. 3, the lubricant pump 1 is shown in a cross-sectional view in a different plane. This cross-sectional view shows one of the lubricant outlets 33. Lubricant can be provided to the lubricant outlet 33 from a metering chamber (not shown in FIG. 4). Another lubricant outlet 33 a is additionally connected to the pressure sensor 75. A pressure sensor monitors the pressure of the entire system composed of grooves and spaces provided in the housing 3, the lubrication piston 27 and the control piston 39. Alternatively, an inductive sensor that detects the movement of the control piston 39 or the lubrication piston 27 instead of the pressure increase in the lubricant outlet 33 may be used.

  A hole 77 is disposed in the fixed disk 37. These holes 77 allow the flow of lubricant. Thereby, the connection to the notch provided in the end caps 5a and 5b is improved. A direction control valve 79 is disposed below the housing 3. The directional control valve 79 can be switched between an inlet and an outlet. The direction control valve 79 includes a magnet portion 81. The direction control valve 79 is operated by the magnet portion 81. Through the hole, the magnet part 81 is also accessible for manual operation.

  The housing 3 is provided with a seal 7. The seal 7 serves to seal the pressure chamber 4a or 4b against the external region as soon as the end caps 5a and 5b are assembled. A lubrication piston 27 is disposed between the pressure chambers 4a and 4b. Lubricating piston 27 has radially distributed holes. A pressure-feed piston 35 is disposed in the hole. A lubricating piston 27 (not shown in FIG. 4) is arranged on the rear side in the axial direction of the fixed disk 37 having a comparable periphery. The pumping piston 35 held by the fixed disk 37 extends in the hole of the lubricating piston 27 in the axial direction to form metering chambers 29a to 29d (see FIGS. 1 to 3). On the basis of the holding of the pumping piston 35 by means of the stationary disk 37, advantageously the rotation of the lubricating piston 27 is prevented. The lubrication piston 27 is fixed with respect to its radial position by a pumping piston 35 fixedly coupled to the housing 3. The fixed disk 37 has a central notch. A control piston 39 is disposed in the notch. As already described with reference to FIGS. 1 to 3, the control piston 39 is movable in the axial direction, and therefore passes through the fixed disk 37 depending on the motion state and position. The control piston 39 is formed in a circular shape in the same manner as the lubricating piston 27 with respect to its outer shape. The control piston 39 additionally comprises at least four surfaces on its radially outer surface in the region of the ends in both axial directions. As a result, the rotation is still prevented. The corners of the control piston 39 may be rounded. However, it must be ensured that the control piston 39 can reciprocate in the fitted state in the lubrication piston 27 and that pressure balance between the pressure chambers 4a and 4b is impossible. A directional control valve 21 is disposed below the housing 3 with a corresponding control unit.

  FIG. 5 shows a circuit diagram of the entire pump assembly. The entire lubricant pump assembly 101 has a feed portion 103 for lubricant under pressure. There is also provided a non-pressure return 105 for the lubricant, which leads to a reservoir not shown in FIG. The original pump 107 is only schematically shown in FIG. The pump 107 has two lubricant connections 109 and 111. The lubricant connection parts 109 and 111 can be connected to the connection parts 103 and 105 alternately via the direction control valve 113. Depending on the position of the directional control valve 113, the pressure connection 103 is connected to the lubricant connection 109 of the pump 107, and at the same time, the lubricant connection 111 is connected to the reservoir via the connection 105 without pressure. Has been. This state corresponds to the illustrated position of the direction control valve 113. When the direction control valve 113 is switched, the pressure connection portion 103 is connected to the lubricant connection portion 111 of the pump 107. Correspondingly, the lubricant connection 109 of the pump 107 is connected to the reservoir via the connection 105 in a non-pressure manner in this operating position via a directional control valve 113.

  The direction control valve 113 can be controlled via a plurality of control lines 115. A pressure line 117 extends from the direction control valve 113 toward the lubricant connecting portions 109 and 111 of the pump 107. Each air line 117 is provided with one air vent line 119. By appropriately connecting the line 117 for guiding the pressure to the pressure connecting portion 103, the lubricant is supplied to the pump 107 in a pressurized state. The pump distributes lubricating oil to the corresponding outlet. In the present embodiment, the pump 107 includes a total of four lubricant connection parts 121, and the lubricant is distributed simultaneously via the four lubricant connection parts 121. The functional principle is as shown in FIGS. A monitoring sensor 123 is disposed on one of the lubricant outlet lines 121. The monitoring sensor 123 monitors the release of lubricant by the pump 107. The monitoring sensor 123 can be read via a plurality of control lines 125.

  Alternatively, an equivalent circuit diagram is created with a corresponding plurality of pumping devices for feeding to a plurality of lubricant outlets.

  FIGS. 6 to 8 show views of the external appearance of the embodiment of the present invention as seen from different directions. In each of FIGS. 6 to 8, an arrow indicating the line-of-sight direction of the other two drawings is shown. FIG. 6 shows a side view of the lubricant pump 201. The lubricant pump 201 includes a housing 203 and end caps 205a and 205b attached to the end side in the axial direction. The end caps 205 a and 205 b are coupled to the housing 203 by a fixing screw 207. The housing 203 has a lubricant connection 209 that is connected to the lubricant line under pressure when the lubricant pump 201 is assembled. Accordingly, the lubricant can be supplied to the lubricant pump 201 via the lubricant connection portion 209 under pressure. Further, the housing 203 has a lubricant connecting portion 211. The lubricant pump 201 can be connected to the lubricant reservoir without pressure via the lubricant connection part 211. A direction control valve 213 is connected to the lower side of the housing. The direction control valve 213 is provided with appropriate wiring for controlling the direction control valve 213 via a plurality of control connections 215. The direction control valve 213 is connected to the lubricant connecting portion 209 and the lubricant connecting portion 211 inside the housing 203. The directional control valve 213 serves to alternately direct the lubricant under pressure at the lubricant connection 209 to a suitable pressure chamber inside the housing 203. Further, a connecting portion 217 is disposed on the housing 203. A sensor is connected to the connection unit 217. With this sensor, the pressure inside one of the plurality of lubricant connections is measured and the normal operation of the lubricant pump 201 is monitored. Above the housing 203, two lubricant outlets 219 are shown at a selected viewpoint. Lubricant under pressure can be supplied to the appropriate lubrication point via the lubricant outlet 219.

  FIG. 7 shows the same embodiment as the embodiment of the invention shown in FIG. 6, but from a different viewpoint. It can be seen that four lubricant outlets 219 are arranged on the upper surface of the housing 203 according to the selected viewpoint. A sensor 217 can be seen on the side of the housing 203. A direction control valve 213 is disposed below the housing 203. From the selected viewpoint, it can be seen that an air vent valve 221 is arranged between the fixing screws 207 in each of the end caps 205a and 205b in order to vent the pressure chamber inside the housing 203.

  FIG. 8 shows a side view of the same embodiment as that of the invention shown in FIGS. FIG. 8 is a plan view of an end cap 205 a including a fixing screw 207 and an air vent 221. Four lubricant outlets 219 are arranged on the upper surface of the lubricant pump 201. A sensor 217 for detecting the pressure in one lubricant outlet 219 is disposed on the right side of the housing. The sensor 217 can also be seen in the cross-sectional view of FIG. A direction control valve 213 is disposed below the end cap 205a. A connection 215 for the control cable is provided laterally from the directional control valve 213.

  FIGS. 9 to 11 show drawings corresponding to FIGS. 6 to 8 of the lubricant pump 201, but a plug connector and a tube connecting portion for the lubricant tube are partially attached. It is illustrated in the state. FIG. 9 shows a side view of the lubricant pump 201. The viewpoint in FIG. 9 is the same as the viewpoint in FIG. A corresponding control cable 251 is connected to the control connection portion 215 of the direction control valve 213. The control cable 251 is connected to one common plug connector 253. Via the plug-in connector 253, the function of the lubricant pump 201 is controlled via a corresponding control unit not shown in FIG. Another line 255, also connected to the control connector 253, is connected to the sensor 217 at one end, allowing the signal of the sensor 217 to be read. One tube connector 257 or 259 having a union nut is connected to the two lubricant connection portions 209 and 211, respectively. Tube connector 257 or 259 serves to connect the lubricant tube directly.

  FIG. 10 is a plan view showing the same embodiment as FIG. The same is true for FIG. 11, which is a side view. 10 and 11 also illustrate the plug connector 253 and the lubricant connections 257 and 259, respectively, with respect to their geometric position. 10 and 11 also show the pressure compensation unit 261 connected to the lubrication tube connecting portion 257 via a T-piece.

DESCRIPTION OF SYMBOLS 1 Lubricant pump 3 Housing 4a, 4b Pressure chamber 5a, 5b Cap 7 Seal ring 9, 11 Lubricant connection part 13, 15 Lubricant passage 17, 19 Lubricant connection part 21 Direction control valve 23, 25 Lubricant path 27 Lubrication Piston 29a, 29b, 29c, 29d Metering chamber 31a, 31b Passage 33, 33a Lubricant outlet 35 Pumping piston 37 Fixed disk 39 Control piston 41a, 41b Control groove 43a, 43b Passage 45 Valve 47 Air vent unit 71 Hole 73 Partial region 75 Pressure sensor 79 Directional control valve 81 Magnet part 101 Lubricant pump assembly 103 Feed part 105 Non-pressure return part 107 Pump 109,111 Lubricant connection part 113 Directional control valve 115 Control line 117 Pressure line 117 Air vent line 121 Lubricant Exit 1 3 Monitoring sensor 125 Control line 201 Lubricant pump 203 Housing 205a, 205b End cap 207 Fixing screw 209, 211 Lubricant connection part 213 Directional control valve 215 Control connection part 217 Pressure sensor 219 Lubricant connection part 221 Air vent valve 251 Control cable 253 Plug connector 255 Line 257,259 Tube connector 261 Pressure compensation unit

Claims (14)

In a device for metering and releasing a lubricant,
A base system with a connection for a line of lubricant;
At least one control piston comprising at least one control element movably disposed in the base system;
At least one lubrication piston comprising at least one metering chamber, which is movably arranged in the base system;
With
The control piston, the lubrication piston and the base system form at least one pressure chamber with a variable volume by movement of the control piston and / or the lubrication piston;
The control piston and / or the lubrication piston are movable in the base system by pressure loading of the pressure chamber;
The control piston and the lubrication piston are formed such that a metering chamber of the lubrication piston can be connected to a lubricant outlet of the base system by the control element by movement of the control piston in the base system. And
When the metering chamber is connected to the lubricant outlet, the lubricating piston is movable within the base system so that the lubricant in the metering chamber is supplied to the lubricant outlet. A device for metering and releasing lubricant   The apparatus of claim 1, wherein the lubrication piston is substantially annular and the control piston is disposed within the lubrication piston.   The device according to claim 2, wherein the control element of the control piston is configured as a groove.   4. The device according to claim 2 or 3, wherein the control piston comprises at least one metering hole, through which each of the pressure chambers can be connected to at least one of the metering chambers.   A valve is disposed in the metering hole, and the valve is formed so that lubricant can be supplied from the pressure chamber into the metering chamber, and backflow of the lubricant is prevented. The apparatus of claim 4.   At least one metering chamber in the lubrication piston is formed by at least one hole, in which a pumping piston coupled to the base system is disposed, the pumping piston being in the metering piston. When a quantity chamber is connected to the lubricant outlet and the lubrication piston moves toward the pumping piston, the volume of the metering chamber is reduced, and the lubricant present in the metering chamber is removed from the lubricant outlet. 6. A device according to any one of claims 1 to 5, wherein the device is adapted to be supplied to the device.   When the lubrication piston moves away from the pumping piston, the volume of the metering chamber can be enlarged, and the lubrication piston and the control piston are connected to the pressure chamber via the metering hole. 7. Apparatus according to any one of claims 4 to 6, which is possible and is arranged such that the metering chamber is filled with lubricant during volume expansion.   Two pressure chambers facing each other with respect to the control piston are provided, and at least one of the metering hole and at least one of the metering chamber and the pressure feeding piston are disposed in each pressure chamber. A device according to any one of claims 4 to 7. An input connection provided in the base system capable of supplying lubricant to the base system under pressure;
A return connection provided in the base system capable of supplying lubricant to the reservoir without pressure;
The device according to any one of claims 1 to 8, further comprising a directional control valve capable of alternately connecting the input connection portion and the return connection portion to each of the pressure chambers. At least two pressure chambers and at least two metering chambers and at least two corresponding metering holes are provided, the pressure chambers being alternately controlled by a lubricant under pressure by appropriate control of the directional control valve. The control piston and the lubrication piston are loadable and each time the pressure load is switched, the following method steps are performed:
The control piston is moved by the pressure in the corresponding pressure chamber each time towards the pressureless chamber,
When reaching the end stopper, by connecting the metering chamber of the lubricating piston disposed in the non-pressure pressure chamber to the lubricant outlet by the corresponding control element,
The lubricating piston is moved by the pressure in the corresponding pressure chamber toward the non-pressure chamber;
Due to the movement, the metering chamber disposed in the pressureless pressure chamber is reduced based on the pumping piston, and the contained lubricant is supplied to the lubricant outlet via the control element,
At the same time, by the movement of the lubricating piston, the volume of the metering chamber of the lubricating piston arranged in the pressure chamber to which pressure is applied is expanded based on the pumping piston, and by the corresponding metering hole, Connected to the pressure chamber to be pressure-loaded, filling the expanding volume of the metering chamber with lubricant,
10. The apparatus of claim 9, wherein the apparatus is configured to perform the method steps.   11. The lubricating piston according to claim 1, wherein the lubricating piston has an axially extending notch disposed in the center, and the control piston is disposed in the notch. The device described.   The device according to any one of claims 1 to 11, wherein the notch and the accommodated control piston are configured to prevent rotation of the control piston about an axial direction.   13. A device according to any one of the preceding claims, wherein a sensor capable of monitoring the movement of the control piston and the lubrication piston is provided. The base system is
A central unit for housing the lubrication piston and the control piston, wherein a track for the lubricant is disposed;
Two end pieces arranged in the central unit on the end side to form the pressure chamber;
14. A pumping piston arranged on the end piece to engage in a corresponding hole in the lubrication piston to form the metering chamber. Equipment.

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