EP2754896B1 - Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments - Google Patents

Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments Download PDF

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Publication number
EP2754896B1
EP2754896B1 EP14150971.1A EP14150971A EP2754896B1 EP 2754896 B1 EP2754896 B1 EP 2754896B1 EP 14150971 A EP14150971 A EP 14150971A EP 2754896 B1 EP2754896 B1 EP 2754896B1
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EP
European Patent Office
Prior art keywords
housing part
spring
gas pump
pump
delivery chamber
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.)
Active
Application number
EP14150971.1A
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German (de)
English (en)
French (fr)
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EP2754896A1 (de
Inventor
Uwe Dr. Meinig
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.)
Schwaebische Huettenwerke Automotive GmbH
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Schwaebische Huettenwerke Automotive GmbH
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Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Priority to EP18187866.1A priority Critical patent/EP3421802B1/de
Publication of EP2754896A1 publication Critical patent/EP2754896A1/de
Application granted granted Critical
Publication of EP2754896B1 publication Critical patent/EP2754896B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/02—Liquid sealing for high-vacuum pumps or for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3442—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face

Definitions

  • the invention relates to a pump for conveying a gas, which is also referred to below as a gas pump.
  • the gas pump is designed as a vacuum pump.
  • the invention aims at a reduction of forces or torques acting on the conveyor on startup of the pump.
  • Vacuum pumps are used in vehicles, for example, to provide negative pressure for a brake booster.
  • the pump can be arranged laterally on the cylinder head of a vehicle engine and driven by a camshaft of the engine, as was customary for a long time. Due to space restrictions and also to reduce the specific size, also in terms of pedestrian protection and costs, the vacuum pump is recently arranged in tandem with a lubricating oil pump, which supplies the vehicle engine with lubricating oil in the oil sump of the lubricating oil system.
  • the lubricating oil pump and the vacuum pump are usually combined in a common housing, and the two pumps have a common shaft in most applications.
  • the US Pat. No. 3,865,515 discloses a coolant pump having a delivery chamber, a delivery rotor rotatably disposed about a rotation axis in the delivery chamber, and a cylinder surrounding the delivery rotor and the delivery chamber.
  • the cylinder and the delivery rotor are arranged in a housing of the pump.
  • an end plate is further arranged, which is pressed by springs against an end face of the cylinder to complete the delivery chamber on the front side.
  • the end plate is axially and tiltably movable in the pump housing, so that at the relevant end face between the cylinder and the end plate can form a relief gap for pressure relief of the delivery chamber. Due to the relief gap, lubricating oil contained in the coolant can escape from the delivery chamber.
  • the lubricating oil is collected in the pump housing and returned to the lubrication points of the coolant pump within the pump housing.
  • the GB 2 092 673 A discloses a coolant pump having a pump housing, a delivery chamber formed in the pump housing, and a delivery rotor rotatably disposed about a rotation axis in the delivery chamber.
  • an end plate is further arranged, which is pressed by springs against an end face of a peripheral wall of the housing to complete the delivery chamber at the end face.
  • the end plate is axially movable in the pump housing, so that between the relevant end face of the peripheral wall of the housing and the end plate, a relief gap for Pressure relief of the delivery chamber can form. Due to the relief gap, liquid coolant and lubricating oil contained in the coolant can escape from the delivery chamber into the housing.
  • the US 4 497 618 A is directed to a pump unit consisting of a hydraulic pump and a tandem-type vacuum pump.
  • the vacuum pump is intended to supply a brake booster of a motor vehicle with negative pressure.
  • the hydraulic pump is used to supply a transmission of a power steering system of the motor vehicle with hydraulic fluid.
  • the hydraulic fluid also serves to lubricate and seal the vacuum pump.
  • the invention is based on a gas pump which has a first housing part with a sealing surface and a second housing part likewise with a sealing surface, furthermore a delivery chamber with an inlet and an outlet for a gas and a delivery device movable in the delivery chamber for conveying the gas.
  • the two housing parts alone can form the delivery chamber with one another, in particular completely enclosing the delivery chamber apart from one or more inlets and one or more outlets.
  • the first housing part and the second housing part it is also possible for the first housing part and the second housing part to enclose the delivery chamber together with one or more further housing parts of the gas pump.
  • the second housing part is a housing cover, which closes off the delivery chamber at one end face.
  • the housing parts are joined together in such a way that they surround the delivery chamber at least partially, preferably completely, over a chamber circumference and abut against each other with said sealing surfaces to form a sealing joint in order to seal the delivery chamber along the chamber periphery over the length of the sealing joint.
  • the sealing surfaces are pressed against each other.
  • the second housing part is movable relative to the first housing part against a pressing force, with which these two housing parts are pressed against each other in the region of the sealing joint, such that the sealing joint can be widened. Due to the expansion, a relief gap is formed by the liquid in the delivery chamber, such as in particular lubricating liquid, can escape.
  • the pressing force is generated by means of a pressing device which presses the two housing parts with said sealing surfaces against each other.
  • the pressing device is set up such that, when a maximum pressure prevailing in the delivery chamber and acting on the second housing part is reached, the pressing force of the pressure device is reached and exceeded as the chamber pressure increases, so that the widening movement of the second housing part and, associated therewith, the widening of the sealing joint commences.
  • the maximum pressure is determined by the pressing device.
  • the pressing device may be arranged so that this expansion movement abruptly depending on a prevailing in the delivery chamber relative to the outer environment of the housing parts overpressure or abruptly when exceeding a predetermined maximum pressure. Accordingly, the discharge gap thus formed can gradually or abruptly closed again with a reduction in the pressure in the delivery chamber and thus the sealing joint can be restored by the pressing force of the pressing device.
  • the second housing part may be flat on a lower side which delimits the delivery chamber on the front side and has the second sealing surface.
  • the second housing part as a whole can be shaped as a plate, preferably as a thin plate. In particular, it may have a wall thickness of at most a few millimeters, preferably from the range of 1 to 6 mm.
  • the second housing part a metal sheet, preferably steel sheet, and in particular be formed by punching as a stamped part or by another separation method.
  • the gas pump is designed as a vacuum pump and serves to supply one or more units of a motor vehicle with negative pressure or is provided for such use.
  • One application to which the invention is directed is that of a vacuum pump for supplying a brake booster or other engine of a motor vehicle with negative pressure.
  • the gas can be air, but in principle also another gas.
  • the gas pump can be designed as a rotary pump.
  • the conveyor as a whole may be rotatable in the delivery chamber about an axis of rotation or comprise at least one in the delivery chamber about a rotation axis rotatable conveyor member.
  • the conveyor may also comprise a plurality of rotatable conveyor members rotatable about spaced apart axes of rotation.
  • the gas pump may be a vane pump and the delivery device may comprise one or more delivery rotors, each having a single or multiple vanes.
  • the pressure prevailing in the pumping chamber in the delivery chamber relative to the environment of the gas pump negative pressure advantageously supports the pressing force.
  • the inlet of the delivery chamber is connected to an aggregate to be supplied with the negative pressure.
  • the outlet of the delivery chamber may be connected to the environment to expel the sucked gas into the environment. Instead, the outlet of the delivery chamber may also be connected to another unit in order to supply it with the gas delivered by the gas pump.
  • the relief gap connects the delivery chamber with the environment of the gas pump or a reservoir for the liquid, closes the delivery chamber so to speak with the environment or the reservoir briefly.
  • the liquid is preferably a lubricating oil for an internal combustion engine, and the engine oil is an internal combustion engine, the relief gap connects the delivery chamber to the lubricant sump or engine oil sump. Due to the connection with the environment or a liquid reservoir into which or the liquid can escape from the delivery chamber, power losses are reduced. The liquid is not further conveyed empty, useless, for example, in circulation of a gas pump designed as a rotary pump.
  • the pressing device generates a spring force which forms at least part of the pressing force.
  • the pressing device can generate the pressing force as a whole as a spring force.
  • the pressing device generates only a part of the pressing force as a spring force and the remaining part in a different manner, for example by means of an electric or hydraulic drive.
  • the generation of the pressing force in the form of a spring force allows structurally simple, inexpensive and particularly reliable versions of the pressing device.
  • the pressing device does not generate the pressing force as a spring force, but only in a different manner, such as electrically or hydraulically.
  • the second housing half must be actively moved to widen the sealing joint by means of the pressing device.
  • the spring force of the pressing device acts the Expansion of the sealing joint and thus acts as a restoring force, which causes a closing of the relief gap with decreasing pressure in the delivery chamber, either in combination with an additional force applied by the pressing device or preferably alone.
  • the pressing device generates at least part of the pressing force as a spring force, it is advantageous if the pressing device is elastically yielding over a spring travel which is at least as great as a largest gap width of the relief gap. This applies both to embodiments in which the pressing force is generated as preferred exclusively as a spring force, as well as for embodiments in which the pressing device applies a spring force in combination with an additional force to keep the sealing joint closed.
  • a stop can be provided, against which the second housing part comes to lie in contact in an end position corresponding to the maximum expansion.
  • the expanding movement of the second housing part may be limited by a spring force counteracting the expansion, increasing during expansion, wherein this spring force limiting the movement may in particular be the pressing force or a part of the pressing force. If the pressing device has one or more spring members for generating said spring force, such a spring member or one or more spring members can not only produce a restoring spring force, but in an additional function also form a fixed stop limiting the movement of the second housing part.
  • the pressing means for generating the pressing force can be fundamentally supported on a supporting device external to the gas pump, embodiments are preferred in which the pressing means only comprise the gas pump or a mounting unit having the gas pump, such as a gas pump and a liquid pump Pump unit, supported.
  • the pressing device for generating the pressing force is supported on the one hand on the first housing part and on the other hand on the second housing part, so that the reaction forces occurring when pressing the second housing part are absorbed by these two housing parts.
  • the pressing device comprises at least one spring member which generates the spring force alone or in combination with one or more optional further spring members of the pressing device.
  • the at least one spring member can in particular be a bending stressed spring or a torsionsbe flyte spring.
  • bending stressed springs come, for example disc springs or diaphragm springs or in particular leaf springs and meandering into consideration, while among the torsionsbe retailten springs, the helical compression springs are preferred. If the pressing device comprises two, three or even more spring members, what has been said applies to each of the plurality of spring members.
  • both a bending-stressed spring and a torsion-stressed spring or leaf springs of different types can be provided.
  • a bending-stressed spring member can be made very easily from a spring plate by a separation process, in particular punching, in combination with at least one forming process and its shape adapted to the geometrical conditions at the installation site.
  • the one or more spring members has or each have a spring support portion and a spring coupling portion.
  • the respective spring member is supported, and in the spring coupling region, it is coupled to the second housing part.
  • it acts in the spring coupling area in the direction of the pressing force on the second housing part.
  • it acts in the spring coupling area directly on the second housing part.
  • the spring member acts via one or more transmission elements on the second housing part, preferably without deflection.
  • the respective spring member may be externally supported in its Federabstütz Scheme with respect to the gas pump.
  • the respective spring member in its Federabstütz Scheme on the first housing part optionally on a third housing part of the gas pump, if one is present, be supported.
  • the respective spring member is supported directly on the first housing part, so that the support does not require a transmission element, but only a corresponding support engagement and preferably simultaneously holding engagement directly from the spring member and the first housing part.
  • the respective spring member can be supported on the first housing part via an additional fastening element, such as a screw element or a press stud element. Such embodiments are appropriate.
  • the one or more spring members of the pressing device can or may each be manufactured separately from the first housing part and the second housing part and coupled to generate the pressing force or at least part of the pressing force at least with the second housing part and be supported on the first housing part.
  • the Spring member or a plurality of spring members of the pressing device may instead be molded in one piece with the first housing part or preferably the second housing part, for example, formed in a casting or sintering process, or firmly joined to a unit with the first housing part or preferably the second housing part.
  • Particularly useful is the formation of a metal sheet, in particular sheet steel.
  • the housing part can be obtained with the one or more integrated spring members, for example by punching as sheet metal stamping or by means of another separation process.
  • the housing part having the spring member integrated in this way or the plurality of spring members integrated in this way may preferably comprise the second housing part, a housing part base structure and either only one or more spring members projecting from this housing part base structure, respectively jointly generated or generate at least a portion of the pressing force.
  • the housing part base structure has the sealing surface of the relevant housing part and can in particular form that part of the relevant housing part which surrounds the delivery chamber.
  • the housing sub-base structure, of which the one spring member protrudes or each protrude more spring members, is advantageously in itself stiff, at least significantly stiffer than the one or more spring members, so that it is not deformed at least in the region of the sealing surface.
  • a plurality of integrated spring members can protrude in particular in the form of a spring arm along a periphery of the housing part base structure.
  • the one or more integral spring members may or may be straight or curved. Bent spring arms is given preference, as this increases the length of the respective spring arm and the spring force generated by the respective spring arm during expansion of the sealing joint can be adapted more accurately to the pressure conditions in the delivery chamber.
  • the respective spring arm can protrude radially or advantageously outwardly in a radial as well as a tangential direction from the periphery of the housing sub-base structure in a plan view of the housing sub-base structure.
  • the respective spring arm is bent in a plan view of the housing sub-base structure, preferably L- or C-shaped, and has a first spring arm portion projecting outwardly from the periphery of the housing sub-base structure and subsequently having a second spring arm portion thereon, at least substantially parallel to the periphery of the housing sub-base structure.
  • the second spring arm section is preferably longer than the first spring arm section.
  • the one or more integrated spring members can or can advantageously be shaped so that it or they stand at a standstill of the pump under a spring preload or each stand and thereby the housing sub-base structure and in particular the sealing surface of this housing sub-base structure press against the other housing part, so that the closed sealing joint is obtained. If this is one or the plurality of spring members are formed separately from the housing parts, such a spring member is preferably mounted with bias, so that it is under a spring bias at standstill of the pump.
  • the integrated spring member may be designed in particular as a bending-stressed spring member. In the case of several integrated spring elements, this advantageously applies to each of these spring elements.
  • the respective integrated spring element is firmly connected to the housing part base structure either in the spring coupling region or in the spring support region.
  • the fixed connection solid connection may, as stated, be a joint connection or advantageously obtained by molding the housing part base structure and the respective integrated spring member in one piece, for example by casting.
  • the one or more integrated spring members may or may be firmly joined to the other of the two housing parts, namely either the first or the second housing part, preferably by means of a releasable connection, such as a screw connection.
  • the housing part which has the one or more integrated spring members, can be shaped overall in the manner of a diaphragm spring or disk spring, wherein this spring totality is advantageously stressed upon expansion of the sealing joint to train and the respective spring member to bending.
  • a respective fastening element such as a screw element
  • the one or more spring members can each simultaneously also form their fastening element, so that a fastening element in addition to the respective spring member is not required.
  • the one or more spring members may each be formed in particular as a spring clip, such as spring plate and have one or two Federabstütz Schemee, with which or each of which engage around the adjacent housing parts and engage behind one of the housing parts, preferably the first housing part.
  • the respective spring member can press directly or indirectly against the other housing part, preferably the second housing part.
  • the respective spring member may cooperate with the two housing parts, in particular in the manner of closure springs, as they are known, for example, for sealing preserving jars.
  • the respective spring member may have a left and a right Federabstweil Scheme.
  • the spring coupling portion extends in such embodiments between these Federabstweil Schemee and connects them together.
  • the spring coupling region may in particular be convexly shaped with respect to the second housing part and act on the second housing part between the spring support areas in the direction of the pressing force, preferably in direct contact against the second housing part.
  • the spring member is offset slightly away from the second housing portion to provide a deflection required for expansion of the second housing portion, i. an elastic yielding to allow the spring member.
  • the respective spring support area can simultaneously form a guide, along which the second housing part in the expansion movement relative to the first housing part in a Leadership intervention.
  • the respective Federabstweil Scheme can engage in the guide engagement between lateral guide elements of the second housing part.
  • the guide elements may be side walls of a recess at the peripheral edge of the second housing part or protruding outwardly protruding projections of the second housing part, into or between which acts as a guide Federabstütz Scheme.
  • the axial clearance of one or more conveyor members of the conveyor is limited by special measures.
  • the gas pump is designed as a rotary pump, for example with one or more peripheral blades, and accordingly has a delivery rotor, its axial play can be limited by a suitable thrust bearing.
  • the housing cover typically limits axial play.
  • the conveying rotor or a wing of a vane-cell type pump can move in the direction of the second housing part during a widening stroke of the second housing part. During the closing movement of the second housing part, this can then press against the conveyor rotor or the wing, which leads to wear. This can be countered by the axial play limitation.
  • the invention may also be a combination of the gas pump according to the invention with a liquid pump, wherein the liquid pump, the supply of an aggregate with a liquid, such as a working fluid or a liquid lubricant, is used, and wherein this liquid also forms the sealing liquid for the gas pump ,
  • the liquid pump may in particular be a lubricant pump for supplying an internal combustion engine or another unit with liquid lubricant.
  • the liquid pump has a delivery chamber and the delivery chamber has an inlet on a low-pressure side of the liquid pump and an outlet for the liquid on a high-pressure side of the liquid pump.
  • the liquid pump further has a drivable conveying device, which can perform a conveying movement in a drive in the delivery chamber, through which the liquid is conveyed from the inlet to the outlet of the delivery chamber.
  • the inlet may be an inlet of the liquid pump upstream of the delivery chamber or an inlet directly into the delivery chamber.
  • the outlet may be an outlet directly of the delivery chamber or an outlet of the fluid pump downstream of the delivery chamber.
  • gas and liquid pump can advantageously be provided to connect a formed in the first or the second sealing surface sealing recess of the gas pump with the low pressure side or the high pressure side of the liquid pump and thereby to supply the liquid in such embodiments serves as a sealing liquid for sealing the sealing joint.
  • the liquid pump has a housing part which forms one or more chamber walls of the delivery chamber of the liquid pump.
  • One of the housing parts of the gas pump can simultaneously also form this housing part of the liquid pump.
  • the housing part in question may in particular comprise the first sealing surface for sealing the delivery chamber of the gas pump.
  • the gas pump and the liquid pump are rotary pumps, so that the conveying device of the gas pump and also the conveying device of the liquid pump each have at least one conveying member rotatable about an axis of rotation, it is also advantageous if these conveying members are rotatably mounted about a common axis of rotation.
  • the at least two rotatable conveyor members may basically surround each other, more preferably they are coaxially juxtaposed.
  • the at least one rotatable conveying member of the gas pump and the at least one rotatable conveying member of the liquid pump may be rotatable relative to each other, in preferred embodiments, however, they are rotatably connected to each other. They are preferably driven together via a drive wheel. They can be coupled by means of a transmission.
  • these conveying members can be arranged on a common shaft.
  • these conveying members with the common shaft each torque be joined.
  • It may also be one of the conveying members, either a conveying rotor of the gas pump or a conveying rotor of the liquid pump, formed with the shaft in one piece and only the other conveying rotor with the shaft rotatably connected.
  • the shaft forms both a conveying rotor of the gas pump and a conveying rotor of the liquid pump in one piece, although in many embodiments this will only be possible with a housing divided in the axial direction.
  • the gas pump may be driven by its own drive motor, for example an electric motor
  • the gas pump is driven by the internal combustion engine and is correspondingly connected to transmit torque to a shaft of the internal combustion engine.
  • the conveyor such as a rotatable impeller of the gas pump, can be connected torsionally rigid with a shaft of the internal combustion engine, i. be rotatably movable relative to the respective shaft and be rotatably driven according to the rotational speed of the respective shaft, when it is in the gas pump as preferred, a rotary pump.
  • a conveyor wheel of the conveyor may be connected via a transmission having the same or different speed than the speed of the machine shaft, i. be driven in rotation via a reduction or transmission gear.
  • the driving machine shaft may be, for example, a crankshaft or camshaft.
  • the internal combustion engine may in particular be an internal combustion engine.
  • the gas pump with inventive pressure relief can be realized alone or in a pump unit in which the gas pump is combined with a liquid pump of the type described in a common housing.
  • the gas pump according to the invention can also be combined with a liquid pump, in particular lubricant pump, wherein the two pumps generally common in motor vehicle construction have separate pump housing and are generally arranged at different locations on or close to the internal combustion engine, and wherein the gas pump the liquid circuit of the liquid pump is connected, so it is at the liquid which is to be able to escape from the delivery chamber of the gas pump according to the invention, is the funded by the liquid pump liquid.
  • the invention also relates to an internal combustion engine with a mounted gas pump or pump unit of the type described and also a vehicle, preferably a motor vehicle, with an internal combustion engine with a mounted gas pump or pump assembly of the kind described.
  • the internal combustion engine can in particular form a drive motor of the vehicle.
  • the gas pump or the pump unit may be at least partially immersed in a lubricant reservoir, in particular in embodiments in which it with a liquid pump for Supply of the internal combustion engine is combined with the lubricant in the described pump unit.
  • FIG. 1 shows a pump unit with a gas pump 10 of a first embodiment and a liquid pump 20 in an isometric view of the gas pump 10.
  • the pump unit comprises a common housing 10 for both pumps 10 and 20. Such arrangements of pumps are also referred to as a tandem arrangement.
  • the common housing comprises a housing part 1, the movable components of the pump unit, in particular a conveyor of the gas pump 10 and a conveyor of the liquid pump 20, movably supports, and housing parts 2 and 27, of which the housing part 2 a cover of the gas pump 10 and the housing part 27th forms a lid of the liquid pump 20.
  • the housing part 1 is integrally molded, suitably cast in one piece. In principle, however, it can also be composed of several pieces instead.
  • the housing parts 2 and 27 are each formed in one piece from metal and joined to the housing part 1, for example, as shown in each case by means of a screw connection.
  • the gas pump 10 and the liquid pump 20 are designed as rotary pumps.
  • the rotary pumps 10 and 20 are arranged coaxially along a common axis of rotation axially one behind the other.
  • the housing part 1 is arranged axially centrally.
  • the housing part 2 is arranged on the one axial end side and the housing part 27 on the other axial end side of the housing part 1.
  • the conveying device of the gas pump 10 comprises a conveying rotor 11, which is rotatable about the axis of rotation, and a single vane 12, which is coupled with the conveying rotor 11 to transmit torque.
  • the conveyor is correspondingly single-leaf.
  • the conveyor rotor 11 guides the wing 12 radially displaceable.
  • the housing part 1 forms in the region of the gas pump 10 a housing pot, which delimits a delivery chamber 3 on one of the liquid pump 20 axially facing chamber front side and surrounds the chamber periphery.
  • the gas pump 10 can be operated in particular as a vacuum or vacuum pump, for example, to supply a brake booster of a vehicle with negative pressure.
  • the brake booster or another or further negative pressure to be supplied unit of the vehicle is connected to the inlet 4, and the sucked gas, preferably air, is discharged via the outlet 5 into the environment, for example in a crankcase of an internal combustion engine.
  • a lubricant serving to lubricate the conveyor 10 is also ejected through the outlet 5.
  • FIG. 1 shows the housing part 2 prior to assembly in a position in which the housing part 2 of the facing open end face of the housing part 1 is axially opposite and pressed to close the delivery chamber 3 only axially against the housing part 1 and must be firmly connected to this.
  • a groove-shaped sealing recess 9 is formed completely circumferentially around the delivery chamber 3.
  • a sealing element 19 for example, a sealing ring is arranged, which is elastically pressed in the assembled state of the housing parts 1 and 2 and thereby ensures the required sealing of the sealing joint.
  • the sealing joint between the sealing surfaces 6 and 7 can also be ensured by a sealing liquid located in the sealing recess 9.
  • the sealing recess 9 is filled in such embodiments at least in pump operation with the sealing liquid. An elastic sealing ring or other sealing element is then not required for sealing the sealing joint.
  • FIG. 2 shows the pump unit of the first embodiment in an isometric view of the liquid pump 20.
  • the liquid pump 20 is like the gas pump 10 of the vane type.
  • the liquid pump 20 comprises a multi-leaf conveyor with a about the common axis of rotation with the gas pump 10 rotatable conveyor rotor 21 and a plurality of distributed over the circumference of the conveyor rotor 21 arranged wings 22.
  • the liquid pump 20 is adjustable with respect to their specific delivery volume. It comprises an adjusting ring 23, which is mounted pivotably relative to the housing part 1 in order to be able to adjust an eccentricity of the conveyor 21, 22 and thereby the specific delivery volume of the liquid pump 20.
  • a restoring spring 26 exerts on the adjusting ring 23 a restoring force acting in the direction of maximum delivery volume.
  • the adjusting ring 23 is acted upon counteracting this restoring force with the conveyed by the liquid pump 20 hydraulic fluid in the direction of a reduction of the specific delivery volume.
  • the vanes 22 divide a delivery chamber of the liquid pump 20 into delivery cells, which increase in rotational drive of the conveyor 21, 22 and eccentric position of the adjusting ring 23 relative to the axis of rotation on a low pressure side of the delivery chamber, whereby liquid is sucked into the delivery chamber, and on a high pressure side shrink the delivery chamber again so that on the High-pressure side through an outlet 25, the liquid is ejected under increased pressure.
  • the inlet region comprises an inlet 24 of the housing part 1, which in FIG. 1 is recognizable, and in the housing part 1 upstream of the feed chamber located inlet portion 24, in which the return spring 26 is arranged by way of example and from which a chamber inlet leads directly into the feed chamber.
  • the outlet region comprises the chamber outlet leading directly from the delivery chamber, furthermore an outlet section 25 formed in the housing part 1 and downstream of this an outlet 25 of the housing part 1.
  • the liquid pump 20 may in particular be a lubricant pump for supplying an aggregate with a liquid lubricant.
  • the liquid pump 20 is a lubricant pump for supplying an internal combustion engine, preferably a drive motor of a vehicle, with liquid lubricant.
  • the pump unit is rotationally driven via a drive wheel 13. If the pump unit is assigned to an internal combustion engine, it can be driven, for example, by a crankshaft of the internal combustion engine via the drive wheel 13.
  • the drive wheel 13 may be part of a traction mechanism or a gear transmission, in principle also be a friction gear.
  • the drive wheel 13 is mechanically coupled to both the conveyor 11, 12 so also with the conveyor 21, 22 and may be rotatably connected in particular with two conveyor rotors 11 and 21.
  • the pump unit may be partially or wholly submerged in a sump or other type of reservoir of a liquid, in particular a reservoir of liquid conveyed by the liquid pump 20.
  • the pump unit can be arranged partially or wholly immersed in a lower region, for example on a lower side, of an internal combustion engine, in the lubricant sump of the internal combustion engine.
  • the arrangement in a liquid reservoir, preferably a lubricant reservoir, is advantageous for the sealing of the gas pump. Due to the prevailing in the pumping operation in the delivery chamber 3 negative pressure lubricant may and may be sucked to a certain extent from the environment, the reservoir, via the sealing joint 6, 7 in the sealing recess 9 and from there into the delivery chamber 3.
  • the outside surrounding the gas pump lubricant which can optionally serve as a sealing liquid at the same time, effectively prevents ambient air in the area surrounded by the lubricant via the sealing joint 6, 7 is sucked, whereby the tightness of the gas pump and thus their efficiency and flow rate can be improved ,
  • FIG. 3 shows the pump unit of the first embodiment in a longitudinal section.
  • FIGS. 3 to 5 show the pump unit of the first embodiment in a longitudinal section ( FIG. 3 ), in a detail ( FIG. 4 ) and in an axial view of the gas pump 10.
  • the housing part 2 is joined to the housing part 1, so that the delivery chamber 3 is tightly closed and the sealing surfaces 6 and 7 together form the sealing joint 8, which surrounds the delivery chamber 3 over the chamber periphery, in that the sealing joint 8 extends around a central longitudinal axis of the delivery chamber 3.
  • the sealing joint 8 is located at an axial end of the delivery chamber 3, in the exemplary embodiment, the sealing surface 6 is an end face at the axially open end of the housing part 2.
  • the housing part 2 is flat over its facing into the delivery chamber 3 end face including the sealing surface 7.
  • the sealing joint 8 for example, at an axially recessed position, a shoulder surface, the housing part 1 or, in principle, the housing part 2 may be formed.
  • sealing joint 8 is still to be noted that this completely, so over 360 °, rotates.
  • the housing part 2 is pressed by means of a pressing device 30 against the housing part 1, so that the sealing surfaces 6 and 7 with the formation of the sealing joint 8 sealingly abut each other.
  • the pressing device 30 is designed such that it permits a movement of the housing part 2 relative to the housing part 1 in a direction axially facing away from the housing part 1, when an opening force acting on the housing part 2 in said direction is greater than the pressing force.
  • the opening force can be generated in particular by a pressure prevailing in the delivery chamber 3 overpressure.
  • the pressing device 30 may in particular be designed so that the pressing force exerted by her while ensuring a sufficient seal over the sealing joint 8 at standstill and in the normal operation of the pump, but on startup of the pump in the delivery chamber 3 due to there befindaji lubricating fluid by the conveying movement the conveying device 11, 12 resulting overpressure causes a widening movement. Because of such an overpressure, the housing part 2 lifts in the region of the sealing joint 8 from the housing part 1 against the restoring pressing force of the pressing device 30, so that the sealing joint 8 expands to a relief gap, pass through the located in the delivery chamber 3 excess lubricating fluid from the delivery chamber 3 and thus can be displaced by the conveyor 11, 12.
  • the pressing device 30 is formed overall as a spring device. It comprises only a single, uniform spring member 31, which is designed and arranged to generate the pressing force as a spring loaded on bending.
  • the spring member 31 is a leaf spring. It consists of a left and right Federabstweil Scheme 32 and a spring coupling portion 33, which extends from the left to the right Federabstweil Scheme 32. All spring portions 32 and 33 are formed in one piece from spring steel, in the example spring plate.
  • the Federabstweile 32 and the spring coupling portion 33 together form a pair of spring clip, such as a spring steel clip, as it is basically known for closing Einmachgläsern.
  • the spring member 31 spans the housing part 2. It engages around the spring support areas 32 an outer circumference of the housing part 2 and a radially outwardly projecting shoulder of the housing part 1. In a central region of the housing part 2, the spring member 31 is coupled to the housing part 2 to In this central area to exert the pressure force generated as a spring force on the housing part 2.
  • the spring member 31 may comprise a plurality of spring arms, for example, three or four spring arms which protrude outwardly from a central spring member portion in the direction of sealing joint 8 and in the direction of the housing part 2 to the spring force uniformly distributed to the housing part 2 and closer to the sealing joint 8 apply.
  • the spring member 31 is convexly formed in the spring coupling portion 33 with respect to the housing part 2.
  • it is a spring plate with a convex profile.
  • the coupling region 33 has the shape of a shallow trough.
  • the spring coupling portion 33 may have an approximately circular convex contour or the shape of a flat "V". It bulges in other words between the Federabstweil Schemeen 32 in the direction of the housing part 2. It presses with a front in the direction of the pressing force against the housing part 2.
  • the spring member 31 is mounted with bias.
  • the spring member 31 bends in its two Federabstweil Schemee 32 from the spring coupling portion 33 each from an enclosed acute angle from. At the free end of the respective Federabstütz Schemes 32 it kinks again to form a holding element 34, as best in FIG. 4 is recognizable.
  • the spring member 31 forms in its Federabstschreib Schemeen 32 each have a flat "U" whose short end leg forms the retaining element 34.
  • With the holding element 34 behind the spring member 31 engages the housing part 1, which has a counter-holding element 35 for the purpose of additional security.
  • the holding elements 34 and holding counter-elements 35 can each pairwise form a latching connection.
  • the kinks can be replaced by softer curves. However, highly curved transitions reduce the space required for the pressing device 30, thus allowing a more compact design.
  • the sealing element 19 may have a diamond profile, so that it can stretch axially over the course of the expansion movement of the housing part 2 over a larger travel, but nevertheless does not prevent the escape of fluid to be displaced by the sealing joint 8.
  • the sealing element 19 in the profile can also be circular or square, but it is preferably orthogonal to the sealing surfaces 6 and 7 but elongated and may for example also be oval. This applies to all embodiments of a gas pump according to the invention with an elastic sealing element such as the sealing element 19.
  • the respective sealing element is preferably arranged with the majority of its measured length in the profile in the sealing recess or secured there by another measure in order to prevent the respective sealing element from being able to be entrained in the case of widened sealing joint 8 by liquid flowing out of the delivery chamber.
  • the housing part 2 can move away from the restoring pressing force of the spring member 31 in a predetermined either by this pressing force or a mechanical stop end position of the housing part 1.
  • the spring member 31 may itself form such a mechanical stop for the housing part 2, should the housing part 2 not already been held due to the increasing pressing force on lifting, or moved again in the direction of the housing part 1.
  • the housing part 2 is guided relative to the housing part 1. This can be done by the pressing device 30, for example, as in the embodiment directly by the spring member 31.
  • the spring member 31 fulfills the guiding function by means of its Federabstweil Schemee 32.
  • the guide is particularly in the synopsis of FIGS. 4 and 5 recognizable.
  • the housing parts 1 and 2 form lateral guide elements 36 and 37 for the Federabstweil Schemee 32 by each having a shallow recess.
  • the Federabstütz Schemee 32 each engage in the associated, in registry with each other located recesses in a guide engagement.
  • the guides 36 and 37 sandwich the spring support portions 32 therebetween.
  • the guide elements 36 of the housing part 1 hold the Spring member 31 in position, and the second housing part 2 is axially guided in the region of the side walls of its guide elements 37 by the spring member 31.
  • the pressing device 30 fulfills in this way the functions of pressing and guiding the housing part 2 and in an advantageous development also a stop for limiting the expansion movement of the housing part second
  • FIGS. 6 to 8 show a pump unit with a gas pump 10 of a second embodiment.
  • the pump unit differs from the first embodiment by a modified pressing device 40. Otherwise, it corresponds to the first embodiment. Apart from the differences described below, reference is therefore made to the comments on the first embodiment.
  • the pressing device 40 has, as in the first embodiment, only a single spring member 41, which is also shaped and arranged as a bending-stressed spring. In contrast to the first embodiment, however, not only provides the spring member 41 for the sufficiently strong, but yielding for the expansion arrangement of the housing part 2.
  • the pressing device 40 has over the spring member 41 addition to a fastening device with fastening elements 44.
  • the spring member 41 corresponds with its coupling region 43 to the spring member 31. However, the left and right outside of the spring coupling region 43 subsequent Federabstütz Schemee 42 shortened and no longer surround the housing parts 1 and 2. Rather, the spring member 41 in its Federabstütz Schemeen 44 by means of fasteners 44th supported on the housing part 1 and also fixed. As regards the spring action or generation and application of the pressing force, the spring member 41 corresponds to the spring member 31st
  • the spring member 41 has a passage for the fastening element 44, which may be formed for example as a screw or pressing bolt.
  • the fastening element 44 first passes through the spring member 41 and then the housing part 2 and projects into a bore of the housing part 1. It can be screwed or pressed in the bore, for example.
  • the fastening element 44 is surrounded in a shaft region between the sealing surface 6 and the Federabstweil Scheme 42 by a sleeve-shaped guide member 45 which projects into the passage formed in the housing part 2 for the fastening element 44 and in the region of the passage to the housing part 2 has a certain play.
  • the game is dimensioned so that the housing part 2 is guided in an expansion movement of the guide member 45, the guide member 45, however, does not hinder the expansion movement.
  • an additional guide member 45 and the fastener 44 in the corresponding shaft portion could Guide housing part 2 directly. Tribologically, however, the use of an additional guide member 45 is advantageous.
  • FIGS. 9 to 11 show a pump unit with a gas pump 10 and a liquid pump 20 in a third embodiment, which is derived from the second embodiment and differs from this only by its Andrück Anlagen 50, so that for explaining the pressing device 50 to the second embodiment and otherwise Reference is made to the first embodiment, in particular also to the explanations of the pressing device 30.
  • the pressing device 50 has a plurality of separate spring members 51, for example, four spring members 51 were selected.
  • the spring members 51 each have a Federabstütz Scheme 52 and then a Federkopplungs Scheme 53, with which they each press against the housing part 2 in order to press this in the region of its sealing surface 7 against the sealing surface 6 of the housing part 1, in particular in detail of FIG. 10 is recognizable.
  • the spring members 51 are supported and fixed in their Federabstweil Schemeen 52 each by means of a fastener 54 on the housing part 1.
  • the fastening elements 54 and guide elements 55 at least substantially correspond to the fastening elements 44 and guide elements 45, so that with regard to the support and fastening of the spring members 51 and the guide of the housing part. 2 Reference is made to the second embodiment.
  • the fasteners 54 and the passages projected through them in the spring support portions 52 may be shaped to form an anti-rotation lock for the respective spring member 51 in cooperation.
  • FIG. 11 This is exemplified for the other spring members 51 only for the lower spring member 51.
  • FIGS. 12 to 14 show a pump unit of a fourth embodiment with a modified pressing device 60.
  • a characteristic feature of the fourth A Embodiment is that spring members 61 of the pressing device 60 are an integral part of the housing part 2. It is in this sense to integrated spring members 61st
  • the housing part 2 has a central, inherently rigid housing sub-base structure 2c and, extending beyond a periphery of the housing sub-base structure 2c, the spring members 61 protrude outwards.
  • the spring members 61 are each formed in the form of a spring arm.
  • the spring arms protrude from the housing part base structure 2c initially a short distance to the outside.
  • Each of the short spring arm sections is adjoined by a longer spring arm section which, at an end remote from the short spring section, merges into a spring support region 62 of the respective spring member 61.
  • each of the spring members 61 has a spring coupling portion 63 projecting freely from the central housing sub-base structure 2c and extending over the major part of its length at least substantially in the circumferential direction.
  • the spring support portions 62 are arranged at the ends of the spring coupling portions 63.
  • the spring members 61 are each immovably fixed relative to the housing part 1.
  • the spring members 61 are in the plan view of FIGS. 13 and 14 at least substantially C-shaped, each having an at least substantially L-shaped spring coupling portion 63.
  • the housing sub-base structure 2c has, on its inner or lower side facing the housing part 1, the sealing surface 7 in order to form the sealing groove 8 of the fourth exemplary embodiment with the axially facing sealing surface 6.
  • the seal groove 8 extends along the periphery of the housing sub-base structure 2c and in the plan view of FIG FIG. 13 radially within the spring members 61.
  • the housing sub-base structure 2c and the spring members 61 are molded in one piece, for example, cast from a metallic material, and optionally reworked, or preferably from a metal sheet, in particular steel sheet, stamped or formed by a different separation process.
  • the housing part 2 forms with the integrated spring members 61 a meander spring whose meandering arms are the spring members 61.
  • the spring members 61 are bending-stressed springs in the form of M througharme.n
  • the housing part base structure 2c may be axially biased by the spring members 61 against the sealing surface 6 of the housing part 1.
  • the spring members 61 may have on their underside a clear distance to the facing end side of the housing part 1 by being there opposite the sealing surface 7 of the housing part 2 (FIG. FIG. 12 ) are a little bit withdrawn.
  • the housing part 2 can be fastened with pretension on the housing part 1.
  • the sealing recess 9 is filled at least during pump operation with a sealing liquid which can be formed in particular by the lubricating liquid for the gas pump 10.
  • the lubricating fluid may be the fluid delivered by the fluid pump 20.
  • the respective sealing recess 9 may be filled with sealing liquid and be dispensed with an elastic sealing element.
  • the liquid seal can be replaced by the arrangement of an elastic sealing element in the sealing recess 9.
  • the sealing by sealing liquid and the supply of the sealing recess 9 with sealing liquid is based on the German patent application no. 10 2012 222 753.9 referred to in this regard.
  • the gas pump of the fourth embodiment and also the entire pump unit corresponds to those of the first embodiment.
  • FIGS. 15 to 17 show a pump unit of a fifth embodiment. Also in this pump unit, a gas pump 10 and a liquid pump 20 are combined to form a mounting unit.
  • the pump unit corresponds to a further modified pressing device 70 apart from the previous embodiments, so again reference is made to the comments on the first embodiment.
  • the pressing device 70 includes as in the third embodiment ( Figures 9-11 ) However, it is not as in the other embodiments to bending-stressed spring members, but each a torsionsbe pipetes spring member 71, for example, each a helical compression spring.
  • the spring members 71 are fixedly connected to the housing part 1 by means of a respective fastening element 74 extending through them. In each case, at their ends remote from the housing parts 1 and 2, they have a spring support region 72 and the housing part 2 facing a spring coupling region 73, as best shown in FIG FIG. 16 can be seen. They are each biased so that they exert a biasing force and in the sum corresponding to the pressing force on the housing part 2 at standstill of the pump.
  • the spring members 71 are distributed along the sealing joint 8 as in the third embodiment, so that they position the housing part 2 relative to the housing part 1 and fix the opening and closing movement relative to the housing part 2 with the for the tight closure of the delivery chamber. 3 apply required pressing force.
  • an axial securing of the conveying rotor 11 and also of the wing 12 is dispensed with.
  • the respective conveying rotor 11 or the respective wing 12 may or may be axially secured in order to prevent the conveying rotor or the wing from moving axially during a widening movement of the housing part 2 and causing a rattling noise.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
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DE102013200410B4 (de) 2017-12-07
DE102013200410A1 (de) 2014-07-17
CN103925189A (zh) 2014-07-16
US11506204B2 (en) 2022-11-22
US20140199199A1 (en) 2014-07-17
EP2754896A1 (de) 2014-07-16
CN103925189B (zh) 2018-01-19
EP3421802A1 (de) 2019-01-02
EP3421802B1 (de) 2022-03-02

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