DE102016212180A1 - Pump, fluid system and internal combustion engine - Google Patents

Pump, fluid system and internal combustion engine

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Publication number
DE102016212180A1
DE102016212180A1 DE102016212180.4A DE102016212180A DE102016212180A1 DE 102016212180 A1 DE102016212180 A1 DE 102016212180A1 DE 102016212180 A DE102016212180 A DE 102016212180A DE 102016212180 A1 DE102016212180 A1 DE 102016212180A1
Authority
DE
Germany
Prior art keywords
pressure
pump
fluid
rotor
lubricant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
DE102016212180.4A
Other languages
German (de)
Inventor
Jessica Wolf
Michael Lüer
Erik Engelen-Krause
Felix Ehrhardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
Original Assignee
Volkswagen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volkswagen AG filed Critical Volkswagen AG
Priority to DE102016212180.4A priority Critical patent/DE102016212180A1/en
Publication of DE102016212180A1 publication Critical patent/DE102016212180A1/en
Application status is Pending legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00Fluid
    • F04C2210/20Fluid liquid, i.e. incompressible
    • F04C2210/206Oil

Abstract

A pump (12) for conveying a fluid comprises a housing (14), a stator (16) and a rotor (18), wherein the stator (16) and the rotor (18) define a delivery space (30) and wherein the rotor (18) the delivery chamber is divided into a low pressure section and a high pressure section and arranged to adjust the delivery volume displaceable with respect to the delivery chamber (30), including the rotor (18) or the stator (16) with the housing (14) has a pressure chamber (38) limited to variable size. According to the invention, the pressure chamber (38) is fluid-conductively connected or connectable to the high-pressure section of the delivery chamber (30). In the case of the pump (12) according to the invention, it is therefore provided to tap off the pressure of the fluid delivered by the pump (12), which is used for a self-regulation of the delivery, as directly as possible in the high-pressure section of the delivery chamber (30). Thereby, a problem can be avoided, which can result from a tapping of the pressure at a considerable distance to an outlet of the pump (12).

Description

  • The invention relates to a pump, in particular a lubricant pump. The invention further relates to a fluid system with such a pump and to an internal combustion engine having such a fluid system.
  • For the supply of internal combustion engines with lubricant usually positive displacement pumps are used. Such lubricant pumps are usually also driven in response to the speed of the lubricant to be supplied with the engine, usually directly or via a mechanical transmission of the internal combustion engines themselves. The delivery speed of such a lubricant pump increases accordingly with the operating speed of the associated internal combustion engine. Since a positive displacement pump basically has a constant specific delivery volume, i. regardless of the delivery speed per revolution promotes substantially the same amount of lubricant, their capacity increases proportionally with the delivery speed and thus with the operating speed of the driving this internal combustion engine. However, the lubricant requirement of an internal combustion engine increases only up to a certain limit operating speed approximately proportional to the operating speed; By contrast, above this limit operating speed, the increase in the lubricant requirement is significantly lower than the increase in the operating speed. Accordingly, such lubricant pumps after exceeding the limit operating speed regularly promote demand. Excess lubricant can then be returned to the sump via a bypass controlled by a pressure relief valve, but with unnecessary energy consumption. In order to avoid a supply of lubricant on demand adjustable lubricant pumps have been developed, which are further driven directly or indirectly by the supplied with lubricant internal combustion engine, but allow additional influencing of the flow rate (in addition to depending on the operating speed of the engine delivery speed).
  • An adjustable lubricant pump in the form of a vane pump or rotary vane pump is for example from the DE 10 2005 034 712 A1 known. In this, in a conventional manner for vane pumps, a multi-wing rotor rotor mounted eccentrically within a stator, between which a sickle-shaped delivery chamber is formed, which is divided by the wings of the rotor into a plurality of pressure chambers, wherein the sizes of these pressure chambers within a revolution of Rotors initially increase, whereby a negative pressure is generated, which leads to a suction of lubricant through a correspondingly positioned pump inlet, and then reduce again, whereby an overpressure is generated, which leads to the desired delivery of the lubricant to the component to be lubricated. The stator itself is displaceably mounted within a housing of the pump, whereby the possibility is provided to change the size of the pressure chambers when they are fluidly connected to the pump inlet and the pump outlet. As a result, the delivery rate of the lubricant pump can be influenced.
  • The lubricant pump according to the DE 10 2005 034 712 A1 On the one hand, it is designed to be self-regulating, for which purpose the pressure of the lubricant conveyed by it is utilized in order to adjust the position of the displaceable stator. A lying above the demand delivery of the lubricant pump thus leads to a corresponding increase in the pressure in the lubricant on the high pressure side of the lubricant pump, resulting in a corresponding displacement of the stator towards a reduced flow rate. In the lubricant pump according to the DE 10 2005 034 712 A1 is the self-regulation of the flow rate by an active control superimposed by an actively controllable actuator is provided, by means of which the stator is also displaced.
  • An adjustable lubricant pump in the form of a gear pump is for example from the DE 10 2007 033 146 B4 known. In this one of the intermeshing gear-shaped rotors is mounted longitudinally displaceable axially, whereby the length of the toothing engagement and thus the size of the effective delivery chamber is adjustable. Also in this lubricant pump, on the one hand, a self-regulation in dependence on the pressure of the delivered lubricant is provided, said self-regulation is actively superimposed by means of a controllable actuator. The lubricant pump according to the DE 10 2007 033 146 B4 serves the promotion of lubricant in a circuit through which components of an internal combustion engine, which serves to drive a motor vehicle, can be supplied with the lubricant. It is provided that the pressure of the lubricant, via which the self-regulation of the pump takes place, in the internal combustion engine and specifically tap downstream of a cooling and cleaning device for the lubricant. This can ensure that the tapped subset of the lubricant, which is supplied to a corresponding control valve for self-regulation, is sufficiently cool and clean, so that an impairment of the function of the control valve can be avoided.
  • In such an integration of a lubricant pump in the lubricant circuit for an internal combustion engine, the problem may arise that the self-regulation of the adjustable lubricant pump based on the tapped pressure of the lubricant is only delayed effect. For example, a conventional lubricant for an internal combustion engine has a high viscosity at low ambient temperatures. This can cause a lubricant pump is operated after a cold start at correspondingly low ambient temperatures short or immediate with a high or maximum capacity, because the lubricant pump driving internal combustion engine is already operated at a correspondingly high operating speed and the thus generated, relatively high hydraulic pressure , which is generated by the lubricant pump, not yet arrived at the control valve due to the high viscosity of the lubricant, which accordingly can not be done reducing the flow rate in the context of self-regulation. This can lead to unacceptably high mechanical loads on the lubricant pump as well as components integrated in the sections of the lubricant circuit immediately following the outlet of the lubricant pump. Also, the pump then generates an unnecessarily high driving resistance for this driving internal combustion engine.
  • The invention was based on the object, with respect to the problem addressed improved fluid system, in particular lubricant system of an internal combustion engine, specify.
  • This object is achieved by means of a fluid system according to claim 4. A pump for such a fluid system and an internal combustion engine with such a fluid system are subject matter of claims 1 and 9. Advantageous embodiments of the pump according to the invention, the fluid system according to the invention and the internal combustion engine according to the invention are objects of the further claims and / or emerge from the following description of the invention ,
  • A pump according to the invention for conveying a fluid comprising at least a housing, a stator and a rotor, wherein the stator and the rotor define a delivery space, and wherein the rotor divides the delivery space into a low pressure section and a high pressure section and displaceable with respect to adjusting the delivery volume the delivery space is arranged (ie by a relative displacement of the stator and rotor, the size and / or shape of the delivery chamber is changed), for which the rotor or the stator (directly or indirectly, ie with the interposition of at least one further element) with the housing a pressure chamber variable Limited size, is characterized in that the pressure chamber is connected directly or indirectly (ie, with the interposition of a functional element influencing a flow of the fluid) fluid-conductively connected to the high pressure section of the pumping chamber or connectable. For this purpose, the pump comprises a corresponding fluid connection, which is preferably integrated as a fluid channel in the housing or is connected as a fluid line to the housing.
  • In the pump according to the invention is therefore provided to tap the pressure of the pumped by the pump fluid, which is used for a self-regulation of the flow rate, as directly as possible in or near the high pressure section of the pumping chamber. Thereby, the described problem can be avoided, which can result from a tapping of the pressure at a considerable distance to an outlet of the pump, wherein in particular also one or more functional elements, which represent a significant flow resistance for the fluid, in the fluid connection between the Outlet of the pump and the point at which the pressure is tapped, can be integrated, whereby this problem is further intensified.
  • A fluid system according to the invention comprises at least one pump according to the invention and at least one fluid circuit in which a fluid can be conveyed by means of the pump.
  • An internal combustion engine according to the invention comprises at least one fluid system according to the invention and an internal combustion engine integrated in the fluid circuit of the fluid system.
  • The fluid system may in particular be a lubricant system, so that for an internal combustion engine according to the invention preferably a fluid connection between the low pressure section of the pump delivery chamber and a lubricant reservoir may be provided. Alternatively, the fluid system may be, for example, a cooling system of the internal combustion engine, wherein the fluid to be delivered may then in particular be a cooling fluid.
  • In a preferred embodiment of the fluid system according to the invention it can be provided that a control and in particular control of the delivery rate of the pump not only via the inventively provided fluid connection between the high pressure section of the pumping chamber and the power control effecting pressure chamber of the pump takes place or can follow, but at least also and preferably primary by means of a further control or regulating device. For this purpose, in a preferred embodiment of the fluid system according to the invention, a control valve can be provided, through which the pressure of the fluid in a pressure chamber of the pump, the rotor or the stator (directly or indirectly) limited to the housing and which has a variable size, is controllable , This pressure chamber can be the same or a different pressure chamber than the one which according to the invention is connected in a fluid-conducting manner to the high-pressure section of the pumping chamber as part of the pump or can be connected.
  • Preferably, a self-regulation of the delivery rate of the pump may be provided by means of the control valve, for which purpose the pressure of the fluid in the corresponding pressure chamber is regulated by means of the control valve in dependence on the pressure which the pump generates. For this purpose, the control valve may have a valve body which can be displaced in a valve housing, the valve body defining (directly or indirectly) with the valve housing a control pressure chamber of variable size, which conducts fluid conductively directly or preferably indirectly (ie with the interposition of a functional element influencing a flow of the fluid to a relevant extent) is connected to the high pressure portion of the pump delivery chamber. In a structurally simple and thus advantageous embodiment of such a control valve can then be provided that the valve body (directly or indirectly) is supported on a spring element such that an increase of the control pressure chamber leads to an increasing bias of the spring element.
  • Preferably, it may be provided that a fluid connection via which the corresponding pressure chamber, controlled by the control valve, can be acted upon by the delivered fluid, leaves the fluid circuit downstream of a fluid connection via which the corresponding pressure chamber is connected or connectable to the high-pressure section according to the invention. Furthermore, at least one functional component influencing the flow of the fluid or the fluid itself, such as in particular a cooling and / or cleaning device for the fluid, can be integrated into a section of the fluid circuit which is arranged between the outlets of these two fluid connections. By a branch of a partial flow of the pumped fluid, by means of which a control or regulation of the delivery rate of the pump can be done using the control valve, downstream of such a cooling and / or cleaning device may affect the functioning of the control valve by a high fluid temperature and / or be avoided by contamination of the fluid.
  • In an internal combustion engine according to the invention, which has such a fluid system, the pressure of the fluid which is applied to the control pressure chamber of the control valve, in particular in a fluid passage of the internal combustion engine can be tapped, because in an operation of the internal combustion engine primarily the required supply of the internal combustion engine with the fluid can be used for the control or regulation of the flow rate of the pump.
  • Alternatively or in addition to a self-regulation of the delivery rate of the pump by means of the control valve can also be provided to actively actuate or influence the control valve, which in particular a (more) more accurate adjustment of the delivery to a variable demand of the fluid to be delivered can take place. For this purpose, in a preferred embodiment of the fluid system according to the invention, an actuator can be provided, by means of which the size of the control pressure chamber of the control valve can be changed.
  • A pump according to the invention may furthermore preferably comprise a pressure-limiting valve, wherein an inlet of the pressure-limiting valve is preferably connected directly to the high-pressure section of the delivery chamber in a fluid-conducting manner.
  • By means of such a pressure limiting valve, on the one hand, a limitation of the pressure on the high-pressure side of the pump can be realized if, despite the regulation according to the invention of the delivery rate, the corresponding pressure of the fluid exceeds a prescribed limit value in certain operating states. For this purpose, it can then be provided that an outlet of the pressure-limiting valve is connected directly or indirectly in a fluid-conducting manner to the low-pressure section of the delivery chamber of the pump. Preferably, a discharge of a portion of the fluid via the then opened pressure relief valve in a fluid reservoir and in particular a lubricant reservoir, which is fluidly connected to the low pressure section of the pumping chamber of the pump, may be provided.
  • Such a pressure limiting valve can additionally or alternatively also serve to allow a control or regulation of the delivery rate to be carried out only secondarily through the fluid-conducting connection of the pressure chamber with the high-pressure section of the delivery chamber by the pressure limiting valve reaching a limit value for the pressure of the fluid in the High pressure section (to the relevant extent) opens and thereby releases the fluid-conducting connection to the corresponding pressure chamber, whereby then a corresponding self-regulation of the flow rate can be realized. For this purpose, it can therefore be provided that the corresponding pressure chamber via the Pressure limiting valve fluidly connected to the high-pressure portion of the pumping chamber is connected or is connected (when the pressure relief valve is open). Such an embodiment of a pump according to the invention is particularly useful if it is to be controlled or regulated in a corresponding fluid system according to the invention primarily by a control valve with regard to the specific delivery rate. Particularly preferably, it can be provided that the corresponding pressure chamber can be connected or connected exclusively to the high-pressure section of the delivery chamber via the pressure-limiting valve, ie, without the interposition of a further functional component.
  • To form a pump according to the invention, which in a structurally simple and thus advantageous manner a control or regulation of the specific delivery rate in response to a pressure of the fluid present in the pressure chamber allows, may preferably be provided that the rotor or the stator so on a spring element is supported, that an increase of the pressure chamber leads to an increasing bias of the spring element. The pressure of the fluid in the pressure space thus operates against a spring element, so that by a relative increase in the pressure, a displacement of the rotor or the stator with respect to the pumping chamber in the direction of increasing or decreasing the capacity can be realized, while a relative reduction of the pressure due then temporarily predominantly restoring force of the spring element leads to such a displacement of the rotor or stator, by which the delivery rate is changed accordingly differently.
  • A pump according to the invention can in particular in the form of a vane pump, as basically in the DE 10 2005 034 712 A1 disclosed, or in the form of a gear pump, as basically in the DE 10 2007 033 146 B4 disclosed, be formed.
  • The indefinite articles ("a", "an", "an" and "an"), in particular in the patent claims and in the description generally describing the claims, are to be understood as such and not as numerical words. Corresponding to this concretized components are thus to be understood that they are present at least once and may be present more than once.
  • The present invention will be explained in more detail with reference to embodiments shown in the drawings. In the drawings shows:
  • 1 : a schematic representation of an internal combustion engine according to the invention and
  • 2 : a detailed view of a pump according to the invention.
  • The 1 shows a schematic representation of an internal combustion engine according to the invention. This includes an internal combustion engine 10 and a fluid system according to the invention with a fluid circuit. The fluid circuit is a lubricant circuit which, among other things, supplies the internal combustion engine 10 with lubricant.
  • In the fluid circuit (or lubricant circuit) of the fluid system (or lubricant system) is also an inventive (lubricant) pump 12 integrated, by which the lubricant is conveyed in the fluid circuit. For this sucks the pump 12 Lubricant from a lubricant reservoir 58 and pushes this under increased hydraulic pressure in the downstream of the pump 12 arranged portion of the fluid circuit.
  • The pump 12 can according to the 2 be designed as variable with respect to the specific capacity variable vane pump. This includes a housing 14 , within which a stator formed annularly in a section 16 is pivotally mounted, wherein the stator 16 a cylindrical inner volume limited within which a rotor 18 is arranged.
  • In the internal combustion engine according to the 1 becomes the rotor 18 the pump 12 directly or with the interposition of a transmission of the internal combustion engine 10 self-propelled. However, there is also the possibility of a different drive of the rotor 18 , For example, by means of a separate drive motor, which may be formed in particular electrically.
  • The rotor 18 includes in addition to a drive shaft 20 a substantially cylindrical body 22 , which rotates with the drive shaft 20 connected is. In a defined division over the circumference of the body 22 a plurality (here seven, for example) are distributed radially and parallel to the axis of rotation 26 of the rotor 18 extending, slot-shaped receiving openings arranged in each of which a wing 24 of the rotor 18 in the radial direction with respect to the axis of rotation 26 are arranged displaceably. One within the main body 22 arranged, annular spring element 28 , consisting of a relatively highly elastic material, acts on the wings 24 of the rotor 18 in the radial outward direction, whereby these with their respect to the spring element 28 distal End faces against the cylindrical inner volume limiting inner wall of the stator 16 are charged.
  • In all possible (swivel) positions of the stator 16 inside the case 14 (except with the exception of a zero position in which the capacity of the pump despite rotating drive of the rotor 16 Zero) is the axis of rotation 26 of the rotor 18 arranged decentrally with respect to the longitudinal axis of the cylindrical inner volume. As a result, between the cylindrical inner volume limiting inner wall of the stator 16 and the lateral surface of the body 22 of the rotor 18 a cross-section sickle-shaped delivery chamber 30 limited, by means of the wings 24 of the rotor 18 is divided into pressure chambers of cyclic variable size.
  • In the 2 is an operating position of the pump 12 shown in the eccentricity of the rotor 18 with respect to the cylindrical internal volume of the stator 16 is maximum, so that the lateral surface of the main body 22 of the rotor 18 at a peripheral portion of the inner wall of the stator 16 almost contacted. In the 2 this is the case approximately in that peripheral portion in which the lowermost wing 24 of the rotor 18 is positioned. This peripheral portion and the peripheral portion offset by 180 degrees to this peripheral portion represent those areas in which the delivery chamber 30 basically by means of the wings 24 of the rotor 18 is divided into a negative pressure section and an overpressure section.
  • In a rotary drive of the rotor 18 in a clockwise direction according to the 2 represents the section of the delivery chamber shown on the left with respect to these peripheral sections 30 the low pressure section, in which the radial width of the delivery chamber 30 in the direction of rotation of the rotor 18 continuously increased, whereby in the pressure chambers, by the located in the vacuum section wings 24 are limited, a negative pressure is generated, which leads to a suction of lubricant via a non-visible fluid inlet, which in the negative pressure portion of the delivery chamber 30 is arranged takes place. In contrast, the radial width of the reduced in the 2 right above pressure section, whereby the hydraulic pressure of the lubricant, which is present in the local pressure chambers, is increased. This leads to a displacement of this lubricant over one in the 2 non-visible fluid outlet in the overpressure section of the delivery chamber 30 is arranged.
  • Due to the maximum possible eccentricity of the rotor 18 with respect to the stator 16 according to the 2 is in the appropriate operating state of the pump 12 also the respective size change in the negative pressure section and the overpressure section of the delivery chamber 30 as far as possible, which corresponds to a maximum specific delivery rate of the pump 12 leads. In this position, the stator 16 that by means of a swivel joint 32 in the case 14 is stored, by means of a prestressed spring element 34 applied.
  • For a change or reduction of the specific delivery capacity of the stator 16 under increasing bias of the spring element 34 from the in the 2 pivoted position shown. This is done hydraulically, by at least one of two pressure chambers 36 . 38 Lubricant is supplied with a hydraulic pressure, taking into account the area over which the hydraulic pressure is effective, to one of the restoring force of the spring element 34 counteracting force that is temporarily greater than this restoring force. A pivoting of the stator 16 takes place so far, until again a balance of power between the hydraulically generated force and with increasing bias of the spring element 34 rising restoring force is reached.
  • A control or regulation of the specific delivery rate of the pump 12 should primarily by means of a variable hydraulic pressure in a first pressure chamber 36 respectively. For this purpose, this hydraulic pressure is tapped by means of a corresponding fluid connection in a section of the fluid circuit which is upstream or inside the internal combustion engine 10 , For example, in a fluid passage in a cylinder head or a cylinder housing of the internal combustion engine 10 integrated, and downstream of a lubricant filter 40 is arranged. In this case, a supply of lubricant in the first pressure chamber 36 by means of a control valve 42 controlled, which is integrated in the corresponding fluid connection. The control valve 42 has one in a valve housing 44 slidable valve body on the valve housing 44 a control pressure chamber 46 limited by variable size, this control pressure chamber 46 via a corresponding portion of the fluid connection with the corresponding portion of the fluid circuit and thus indirectly with the high pressure portion of the pump 12 connected is. The hydraulic pressure of the lubricant in the control pressure chamber 46 of the control valve 42 generates a force on the valve body, the restoring force of a prestressed spring element 48 of the control valve 42 counteracts. Exceeds this hydraulically generated force due to the pumping of lubricant 12 above the needs of the internal combustion engine 10 the restoring force of the spring element 48 so far that the control valve 42 is switched, the first pressure chamber 36 connected to the corresponding section of the fluid circuit. The thus generated relatively high hydraulic pressure in the first pressure chamber 36 then leads to a pivoting of the stator 16 inside the case 14 the pump 12 and consequently to a reduction of the specific delivery rate of the pump 12 depending on the actual hydraulic pressure in the corresponding section of the fluid circuit. By means of the control valve 42 becomes
  • Consequently, a self-regulation of the specific capacity of the pump 12 depending on the hydraulic pressure of the pump 12 promoted lubricant implemented.
  • In order to adapt the absolute delivery rate of the pump as exactly as possible 12 to the lubricant requirement of the internal combustion engine 10 (And possibly other components to be lubricated, which are integrated into the fluid circuit) to reach, the control valve 42 additionally also by means of an actively controllable actuator 50 be switched. In this case, a driving of the actuator 50 in particular as a function of different (measured or determined in another way) operating parameters of the internal combustion engine by means of a control device, not shown, (in particular a motor control of the internal combustion engine) take place.
  • In particular, after a cold start of the internal combustion engine at relatively low ambient temperatures and consequently at a relatively high viscosity of the lubricant, it may happen that the pump 12 as a result of a short-term or immediately after the cold start present drive the internal combustion engine 10 with relatively high operating speeds and in combination with the by the spring element 34 adjusted position of the stator 16 , which leads to a maximum specific delivery, has a relatively high absolute delivery rate, due to the relatively poor flowability of the lubricant to a high hydraulic pressure in the high pressure section of the pump 12 and in the directly adjoining section of the fluid circuit (in particular in which up to the lubricant filter 40 extending portion), while the hydraulic pressure in that portion of the fluid circuit in which the control valve 42 integrating fluid connection goes off, well below. This leads to a comparatively high mechanical load of the pump 12 and the fluid lines in which are attached to the pump 12 immediately adjacent section of the fluid circuit and to an unnecessarily high drive resistance for the internal combustion engine 10 that by the pump 12 is produced. Since the hydraulic pressure in the portion of the fluid circuit in which the the control valve 42 integrating fluid line, then significantly lower than in the high pressure section of the pump 12 is, can about the hydraulic pressure in the first pressure chamber 36 no suitable regulation of the specific delivery rate of the pump 12 be achieved.
  • To avoid this disadvantage is a pressure relief valve 52 in direct and as short as possible a connection with the high-pressure section of the delivery chamber 30 intended. At the pump 12 according to the 2 is the pressure relief valve 52 in the case 14 the pump 12 self-integrated. The pressure relief valve 52 , which is preferably designed in the form of a simple check valve, opens when exceeding a limit value of the hydraulic pressure in the high pressure section of the pumping chamber 30 and thereby directs a portion of the pump 12 conveyed lubricant in the second pressure chamber 38 The stator 16 together with the housing 14 limited. This leads to a pivoting of the stator 16 under increasing bias of the spring element 34 the pump 12 towards a lower specific delivery rate. Because the second pressure chamber 38 with lubricant, the hydraulic pressure of which substantially corresponds to the hydraulic pressure in the high-pressure section of the delivery chamber 30 corresponds to existing lubricant, the delayed after a cold start effect of regulating the specific capacity of the pump 32 by means of the hydraulic pressure in the first pressure chamber 36 compensates and consequently a mechanical overload of the pump 12 and the directly to the high pressure section of the delivery chamber 30 subsequent components of the fluid circuit and an unnecessarily high drive resistance, the pump 12 in retroaction to the internal combustion engine 10 affects, avoided.
  • The lubricant filter 40 the internal combustion engine according to the 2 is by means of a check valve 54 controlled by-pass 56 designed to bypass, in particular at a clogging of the lubricant filter 40 an uninterrupted and sufficient supply of the internal combustion engine 10 to ensure with the lubricant.
  • Furthermore, in the 2 shown that there is also the possibility of both the control valve 42 as well as the pressure relief valve 52 with the same pressure chamber 36 . 38 the pump 12 connect to.
  • LIST OF REFERENCE NUMBERS
  • 10
    internal combustion engine
    12
    (Lubricant) Pump
    14
    casing
    16
    stator
    18
    rotor
    20
    drive shaft
    22
    body
    24
    wing
    26
    axis of rotation
    28
    Spring element of the rotor
    30
    delivery chamber
    32
    pivot
    34
    Spring element of the pump
    36
    first pressure chamber
    38
    second pressure chamber
    40
    lubricant filter
    42
    control valve
    44
    valve housing
    46
    Control pressure chamber
    48
    Spring element of the control valve
    50
    actuator
    52
    Pressure relief valve
    54
    check valve
    56
    bypass
    58
    lubricant reservoir
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 102005034712 A1 [0003, 0004, 0004, 0023]
    • DE 102007033146 B4 [0005, 0005, 0023]

Claims (10)

  1. Pump ( 12 ) for conveying a fluid with a housing ( 14 ), a stator ( 16 ) and a rotor ( 18 ), wherein the stator ( 16 ) and the rotor ( 18 ) a delivery room ( 30 ) and where the rotor ( 18 ) subdivides the delivery chamber into a low-pressure section and a high-pressure section and displaceable with respect to the delivery chamber (FIG. 30 ), to which the rotor ( 18 ) or the stator ( 16 ) with the housing ( 14 ) a pressure chamber ( 38 ) of variable size, characterized in that the pressure space ( 38 ) fluid-conducting with the high-pressure section of the delivery chamber ( 30 ) is connected or connectable.
  2. Pump ( 12 ) according to claim 1, characterized by a pressure relief valve ( 52 ), wherein an inlet of the pressure relief valve ( 52 ) with the high-pressure section of the delivery chamber ( 30 ) is fluid-conductively connected.
  3. Pump ( 12 ) according to claim 2, characterized in that the pressure space ( 38 ) via the pressure relief valve ( 52 ) fluid-conducting with the high-pressure section of the delivery chamber ( 30 ) is connectable.
  4. Fluid system with a pump ( 12 ) according to one of the preceding claims and with a fluid circuit in which a fluid is pumped by means of the pump ( 12 ) is eligible.
  5. Fluid system according to claim 4, characterized by a control valve ( 42 ), by which the pressure in a pressure chamber ( 36 ) of the pump ( 12 ), the rotor ( 18 ) or the stator ( 16 ) with the housing ( 14 ) and which has a variable size, is controllable.
  6. Fluid system according to claim 5, characterized in that the control valve ( 42 ) one in a valve housing ( 44 ) has displaceable valve body, wherein the valve body with the valve housing ( 44 ) a control pressure space ( 46 ) of variable size, the fluid-conducting with the high-pressure section of the delivery chamber ( 30 ) is connected or connectable.
  7. Fluid system according to claim 6, characterized in that the valve body on such a spring element ( 48 ) is supported, that an increase of the control pressure space ( 46 ) to an increasing bias of the spring element ( 48 ) leads.
  8. Fluid system according to one of Claims 4 to 7, characterized by an actuator ( 50 ), by which the size of the control pressure space ( 46 ) is changeable.
  9. Internal combustion engine with a fluid system according to one of Claims 4 to 8 and with an internal combustion engine integrated into the fluid circuit ( 10 ).
  10. Internal combustion engine according to claim 9, characterized by a fluid connection between the low pressure section of the delivery chamber ( 30 ) and a lubricant reservoir ( 58 ).
DE102016212180.4A 2016-07-05 2016-07-05 Pump, fluid system and internal combustion engine Pending DE102016212180A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102016212180.4A DE102016212180A1 (en) 2016-07-05 2016-07-05 Pump, fluid system and internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016212180.4A DE102016212180A1 (en) 2016-07-05 2016-07-05 Pump, fluid system and internal combustion engine

Publications (1)

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DE102016212180A1 true DE102016212180A1 (en) 2018-01-11

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005034712A1 (en) 2005-07-26 2006-02-16 Daimlerchrysler Ag Controllable oil pump for an engine has a geometrical chamber, a first actuator, a second electromechanically triggerable actuator and a control device
DE112007001037T5 (en) * 2006-05-04 2009-04-02 Magna Powertrain Inc., Concord Vane pump with variable displacement and two control chambers
DE102007033146B4 (en) 2007-07-13 2012-02-02 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Adjustment valve for adjusting the delivery volume of a positive displacement pump
DE102013224208A1 (en) * 2012-11-27 2014-05-28 Hitachi Automotive Systems, Ltd. variable
DE112015001797T5 (en) * 2014-04-14 2017-01-19 Magna Powertrain Inc. Adjusting pump with hydraulic passage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005034712A1 (en) 2005-07-26 2006-02-16 Daimlerchrysler Ag Controllable oil pump for an engine has a geometrical chamber, a first actuator, a second electromechanically triggerable actuator and a control device
DE112007001037T5 (en) * 2006-05-04 2009-04-02 Magna Powertrain Inc., Concord Vane pump with variable displacement and two control chambers
DE102007033146B4 (en) 2007-07-13 2012-02-02 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Adjustment valve for adjusting the delivery volume of a positive displacement pump
DE102013224208A1 (en) * 2012-11-27 2014-05-28 Hitachi Automotive Systems, Ltd. variable
DE112015001797T5 (en) * 2014-04-14 2017-01-19 Magna Powertrain Inc. Adjusting pump with hydraulic passage

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