EP2440785B1 - Lubricant pump system - Google Patents

Description

The present invention relates to a map-controlled lubricant pump system with a lubricant pump for supplying an internal combustion engine with lubricant. The invention also relates to a lubricant pump for such a map-controlled lubricant pump system.

From the WO 2008/037070 A1 is a map-controlled lubricant pump system with a lubricant pump, in particular a cell pump, known for supplying an internal combustion engine with lubricant. The lubricant pump is controlled by a proportional valve, which is connected on the input side to the internal combustion engine. In the lubricant pump while a biased by a spring adjusting unit is arranged, via which a delivery rate of the lubricant pump is controlled. On the adjusting unit acts a first pressure chamber, which is also arranged in the lubricant pump and can be acted upon with pressure and thereby adjusts the adjusting unit against the spring and which the proportional valve is connected upstream.

From the US 2007 / 0224067A1 In turn, a lubricant pump system with a designed as a vane pump lubricant pump is known.

Also from the WO 2007 / 128105A1 is known as a vane pump lubricant pump known.

Finally, out of the WO 2008 / 030491A2 a lubricant pump system known with a lubricant pump in which a pump sensor between the Proportional valve and the internal combustion engine or a control unit thereof is arranged.

The use of volume-controlled lubricant pumps in internal combustion engines is state of the art, for example, to be able to approximate a flow rate and a pressure to the needs of the respective needs of the internal combustion engine. This is usually done by applying an actuating unit within the lubricant pump, such as a control piston or a collar, with an originating from a Hauptölgalerie the engine oil pressure. The disadvantage of such a control is that the control is in direct connection of the pressure prevailing in the engine oil pressure, the flow rate, an engine speed, a lubricant temperature and a voltage applied to the actuator spring force. The aim of so-called characteristic map controls is the decoupling of said direct influencing variables on the control in order to achieve a control map of the lubricant pump, which can respond to each individual influencing variable, thus coming closer to the needs of the internal combustion engine and at least reduce further drive and power losses. For this purpose, usually proportional valves are used which switch on or off a control oil pressure from the main oil gallery or from an outlet of the lubricant pump as needed to the actuators.

If it comes to controls in such a control loop or to a defect of the proportional valve, this can lead to a shortage of the internal combustion engine and thus to damage the same. For this reason, a kind of emergency control is provided at a higher pressure level in the usual lubricant pumps to continue with the internal combustion engine in case of failure of the proportional valve Supply lubricant. Such a so-called "second-level valve", which is a kind of piston valve, is acted upon by both sides with lubricant pressure and biased on the one hand with a spring to hold the actuator in a preferred position, so that the control pressure from the proportional valve directly to the Actuator of the lubricant pump can act. In case of a defect of the proportional valve, the lubricant pump gets no Abregeldruck on the proportional valve and thus promotes the maximum possible flow in the main oil gallery of the engine. In this case, the second-level valve is acted upon only on one side by the increasing lubricant pressure of the main oil gallery and at the same time assumes a position in which the lubricant, ie the oil, of the main oil gallery can flow in and out of the actuating unit as a function of the oil pressure and thus regulates the lubricant pump to a desired higher pressure level. However, a disadvantage of such a lubricant supply system is a high number of parts with associated high assembly, storage and logistics costs.

The present invention is concerned with the problem of providing a map-controlled lubricant pump system, which operates reliably and at the same time is inexpensive to implement.

This problem is solved according to the invention by the subject matter of independent claim 1. Advantageous embodiments are the subject of the dependent claims.

The present invention is based on the general idea of eliminating a previously conventional "second-level valve" by a corresponding design of a lubricant pump in a map-controlled lubricant pump system with a lubricant pump. In the invention map-controlled lubricant pump system of the actual lubricant pump is preceded by a proportional valve, which is the input side connected to the internal combustion engine and / or communicating with an output of the lubricant pump. Within the lubricant pump according to the invention, a spring-biased actuating unit, for example a ring or a slide, is arranged, via which a delivery rate of the lubricant pump, which is usually designed as a cell pump, can be regulated. In this case, the lubricant pump according to the invention has a first pressure chamber acting on the setting unit, which can be acted upon by pressure under characteristic map control and thereby displaces the setting unit against the spring and at least two second pressure chambers acting in the same way on the setting unit. The second pressure chambers are dimensioned smaller than the first, so that in case of failure of the proportional valve, the lubricant pump is pressurized exclusively via the at least two second pressure chambers and due to their smaller dimension, a higher lubricant pressure, that is, a higher oil pressure generated, so that the internal combustion engine is supplied with lubricant at a higher pressure level when the proportional valve fails. In this case, a permanently applied lubricant pressure acts on the first pressure chamber, as well as on the two second pressure chambers, wherein the ratio of the two pressure chambers and the spring biasing the actuator is designed so that the permanently applied lubricant pressure and the supplied via the proportional valve lubricant pressure the complete Map covers. The two second permanently impinged pressure chambers are dimensioned so that in case of failure of the proportional valve, so the sole concern of the permanent lubricant pressure at the second pressure chambers, the lubricant pump due to the constant spring counterforce on the actuator continues to operate at a higher pressure level and the internal combustion engine Lubricant, that is supplied in particular with oil. Of particular advantage is that by eliminating the previously separately trainee "second-level valve" and the elimination of all necessary edits in a valve area significantly fewer items are present, which would also have to be laboriously mounted. The lubricant pump system according to the invention thus has a lower variety of parts and associated lower storage and logistics costs and lower installation costs. In addition, eliminating the second-level valve eliminates interactions with the actuator. Furthermore, the map-controlled lubricant pump system according to the invention works in case of failure of the proportional valve at a higher balance of forces, which minimizes the influence of internal forces from a pump running set. Of course, the lubricant pump according to the invention can also be used elsewhere, so that the lubricant pump system according to the invention relates to a map control of all hydraulically variably controllable lubricant pumps for internal combustion engines with second-level control. The factors such as lubricant pressure, volume flow, engine speed, lubricant temperature and the spring force applied to the actuator can be taken into account separately.

Map-controlled means that, contrary to the two-stage or multi-stage control, the proportional valve is not "only" added or disconnected, and thus the additional pressure or control chamber is subjected to control pressure. Here, the temperature, the speed, the oil pressure, the load case, etc. of the unit to be supplied, for example, an internal combustion engine, determined and compared with a predetermined map (control system). Then the proportional valve is frequency-modulated controlled (uppulled) and placed on the basis of the respective position of the proportional valve, the actuating unit of the lubricant pump in a certain position, that of the lubricant pump allows the flow rate and discharge pressure to be displayed according to the given "characteristic field". In conventional multi-stage controls, the control pressures in direct dependence on oil temperature (medium temperature), speed u. the given geometries of the (pressure) chambers. Here only the pressure chambers are added.

In the known map control of the control pressure is interrupted on the setting unit of the lubricant pump in case of failure of the proportional valve. The lubricant pump thus goes to full delivery, the pump output pressure rises until the pump outlet pressure opens the second-level valve and supplies the lubricant pump with control pressure internally. The interpretation of the SLR valve is that this opens or closes at a correspondingly higher pressure than the normal working pressure of the lubricant pump and regulates the lubricant pump at this pressure level and supplies the internal combustion engine accordingly. Disadvantages here are the interactions of the different mass-force systems of second-level valve and actuator, which can lead to interactions up to the swinging of the entire second-level control and actuator. In contrast, the lubricant pump according to the invention is continuously supplied with control pressure which corresponds to the SLR level. One advantage is that the lubricant pump can be controlled with pump output pressure (controlled internally) or with the pressure from the main supply channel and any points in the supply circuit. The map control system controls the proportional valve at high frequency and due to the respective position of the proportional valve, another actuating range is provided with pressure to the already existing SLR pressure range and brought the adjustment of the lubricant pump in a certain position, which allows the lubricant pump, flow rate and discharge pressure to represent the given "map".

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Fig. 1

ein erfindungsgemäßes Schmierstoffpumpensystem,

Fig. 2

eine Schnittdarstellung durch eine nicht zur Erfindung gehörenden Ausführungsform einer Schmierstoffpumpe,

Fig. 3

eine Darstellung wie in Fig. 2, jedoch bei einer anderen Ausführungsform,

Fig. 4

eine weitere nicht zur Erfindung gehörende Ausführungsform der Schmierstoffpumpe.

Show, in each case schematically,

Fig. 1

a lubricant pump system according to the invention,

Fig. 2

a sectional view through a not belonging to the invention embodiment of a lubricant pump,

Fig. 3

a representation like in Fig. 2 but in another embodiment,

Fig. 4

another not belonging to the invention embodiment of the lubricant pump.

According to the Fig. 1 , has a map-controlled lubricant pump system 1, a lubricant pump 2, which is for example designed as a cell pump, and which serves to supply an internal combustion engine 3 with lubricant. Within the lubricant pump system 1 according to the invention, a filter 4 connected to an output side of the lubricant pump 2, a pressure sensor 5 and a proportional valve 6 are also arranged, the latter for example as a 3/2-way valve can be trained. Of course, the lubricant pump system 1 according to the invention also includes a lubricant reservoir 7 in which the lubricant, for example the oil 8, is collected. Regardless of whether oil 8 is mentioned below, this naturally also includes any other common lubricant.

To control the power of the lubricant pump 2 serves the proportional valve 6, which is the input side connected to the engine 3 and an output of the lubricant pump 2 communicating. If one considers in particular the Fig. 3 , it can be seen that within the lubricant pump 2, an adjustable adjusting unit 9 is arranged, via which a delivery rate of the lubricant pump 2 is controlled, and which is biased by a spring 10. In contrast to a spring force of the spring 10, an oil pressure acts which acts via a first pressure chamber 11 acting on the setting unit 9 as well as via at least two second pressure chambers 12, 12 '. As here in particular the Fig. 2 it can be seen, is the second pressure chamber 12, smaller dimensioned than the first pressure chamber 11 and in the presence of two pressure chambers 12, 12 'according to Fig. 3 Both the first pressure chamber 11 and the at least one second pressure chamber 12, 12 'is acted upon by a map controlled oil pressure and adjusted depending on the introduced oil pressure the actuator 9 against the spring force of Spring 10.

The first and / or the second pressure chamber 11, 12, 12 'are communicatively connected on the input side to the internal combustion engine 3 and / or to an output of the lubricant pump 2, wherein in accordance with the Fig. 3 shown lubricant pump 2 a total of two second pressure chambers 12, 12 'are provided, which are connected to each other via a connecting channel 13.

In case of failure of the proportional valve 6, the lubricant pump 2 is pressurized exclusively via the second pressure chambers 12, 12 ', wherein due to the smaller dimensions of the second pressure chambers 12, 12', a higher lubricant pressure is generated, so that the internal combustion engine 3 even in the event of failure Proportional valve 6 on the one hand sufficiently supplied with lubricant, on the other hand, however, takes place at a relatively higher pressure level.

According to the Fig. 2 the actuator 9 is pivotally configured while, according to the Fig. 3 is designed as a translationally adjustable slider. Due to the map-controlled lubricant pump system 1 according to the invention, a hitherto required "second-level valve" can be dispensed with, as a result of which fewer parts are produced and mounted and thus the entire lubricant pump system 1 can be made more cost-effective. In addition, interactions of the now omitted second-level valve can be excluded with the actuator 9, wherein the lubricant pump system 1 according to the invention also in its second-level control, in which only the second pressure chambers 12, 12 'are pressurized, on a higher balance of forces works, which minimizes the influence of internal forces from a pump running set. Moreover, with the lubricant pump 2 according to the invention, all factors such as oil pressure, volume flow, engine speed, oil temperature and spring force can be taken into account separately from each other without an additional second-level valve. The proportional valve 6 serving to control the lubricant pump 2 in the normal operating state is connected on the input side via a main oil gallery to the internal combustion engine 3 or to the outlet of the lubricant pump 2.

According to the Fig. 4 , A lubricant pump 1 a has a shaft 2 a, on which a rotor 3 a is arranged rotationally fixed. The rotor 3a is operatively connected via a single pendulum 4a with a cage 5a, wherein the cage 5a is guided in a slide 6a. The slider 6a in turn is pivotally mounted about a bearing pin 7a and biased by a spring 8a. The spring 8a, for example a control spring, is supported at one end on the slide 6a and at the other end against a spring counterpart 9a on the housing 10a of the lubricant pump 1a. By rotating the slider 6a about the bearing pin 7a, a capacity of the lubricant pump 1a according to the invention can be regulated, for example, by changing the volumes of a pressure chamber 11a and a suction chamber 12a by changing the eccentricity of the rotor 3a to the slider 6a. The lubricant pump 1a is designed as a so-called cell pump and is usually used to supply an internal combustion engine, not shown, with lubricant, in particular with oil.

An adjustment of the slide 6a is effected by means of a hydraulic pressure within a control pressure chamber 14a, wherein an increase in the pressure in the control pressure chamber 14a causes an adjustment of the slide 6a against the spring 8a. In addition, the slide 6a still separates a damping chamber 13a from a suction chamber 17a, wherein a separation between the control pressure chamber 14a, the damping chamber 13a and the suction chamber 17a via arranged on the slide 6 sealing strips 15a and 15a ', which the slider 6a relative to the housing 10a the lubricant pump 1 a seal.

Between the control pressure chamber 14a and the damping chamber 13a is according to a first variant, a connection 16a, for example a connecting channel, to compensate for pressure fluctuations and thus to Damping of the lubricant pump 1 a provided. The connection 16a can not only be designed as a connecting channel formed in the housing 10a, but also be integrated as a channel in the manner of a freischliff or already in the cast housing, between the slide 6a and the housing 10a. The connection 16a is according to the Fig. 1 shown greatly enlarged so that it is usually designed so small that it unfolds a throttle effect. As an alternative to the connection 16a, a connection 16a 'may also be provided between the damping chamber 13a and the suction chamber 17a, this connection 16a' extending within the slide 6a and, in this case, also being designed as a connecting channel. Of course, in this case too, a connection between the damping chamber 13a and the suction chamber 17a may alternatively be formed as a clearance between the slider 6a and the housing 10a, overcoming the sealing strip 15a '.

Both variants have in common that any pressure fluctuations or pressure pulsations occurring through the connection 16a or 16a 'better balanced and thus can be compensated, whereby a damping of the vibrations occurring in the lubricant pump 1a of the slide can be achieved. The control pressure chamber 14a is usually smaller than the damping chamber 13a and is at the same time usually connected on the input side to a main oil gallery of the internal combustion engine.

A further alternative is to connect a damping volume (lubricant reservoir 18a) mounted outside the housing 10a to one of the volumes in the pump by means of a throttle bore acting like the connection 16a, 16a '.

Through the connection 16a, an overpumping of the oil is achieved from one to the other volume in all embodiments, at the same time there is a throttling whereby the pressure pulsations are reduced.

Claims (7)

1. A characteristic-map-controlled lubricant pump (2), in particular a rotary vane pump, for a lubricant pump system (1),

   - with a spring-loaded actuating unit (9), via which a delivery output of the lubricant pump (2) is controllable,

   - with a first pressure chamber (11) acting on the actuating unit (9), which is arranged in the lubricant pump (2) and pressurized in a characteristic-map-controlled manner and because of this, adjusts the actuating unit (9) against the spring (10),
   characterized in that two second pressure chambers (12, 12') are provided, which are arranged in the lubricant pump (2) and are likewise pressurized and because of this adjust the actuating unit (9) against the spring (10) and which are communicatingly connected to one another via a connecting channel (13), wherein the two second pressure chambers (12, 12') in total are dimensioned smaller than the first pressure chamber (11).
2. A characteristic-map-controlled lubricant pump system (1) with a lubricant pump (2), in particular a rotary vane pump, according to Claim 1 for supplying an internal combustion engine (3) with lubricant, in particular with oil,

   - wherein the lubricant pump (2) is controlled by a proportional valve (6), which is connected in a communicating manner on the input side to the internal combustion engine (3) and/or an output of the lubricant pump (2),

   - wherein the proportional valve (6) is connected upstream of the first pressure chamber (11) acting on the actuating unit (9), which is arranged in the lubricant pump (2) and pressurized in a characteristic-map-controlled manner and because of this adjusts the actuating unit (9) against the spring (10),
   characterized in that upon a failure of the proportional valve (6) the lubricant pump (2) is exclusively pressurized via the at least second pressure chambers (12, 12') and because of its smaller dimensions generates a higher lubricant pressure, so that the internal combustion engine (3) is adequately supplied with lubricant even upon a failure of the proportional valve (6).
3. The lubricant pump system according to Claim 2, characterized in that the first pressure chamber (11) and/or at least one second pressure chamber (12, 12') is/are connected in a communicating manner on the input side to the internal combustion engine (3) and/or an output of the lubricant pump (2).
4. The lubricant pump system according to Claim 2 or 3, characterized in that between the proportional valve (6) and the internal combustion engine (3) a pressure sensor (5) is arranged.
5. The lubricant pump system according to any one of the Claims 2 to 4, characterized in that on the output side of the lubricant pump (2) a filter (4) is provided.
6. The lubricant pump system according to any one of the Claims 2 to 5, characterized in that the proportional valve (6) on the input side is connected to the internal combustion engine (3) via a main oil gallery.
7. The lubricant pump system according to Claim 6, characterized in that the first pressure chamber (11) is indirectly connected to the main oil gallery via the proportional valve (6) and at least one second pressure chamber (12, 12') is directly connected to the main oil gallery.

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