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EP0225338B1 - Pompe a capacite variable - Google Patents

Pompe a capacite variable Download PDF

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Publication number
EP0225338B1
EP0225338B1 EP86902794A EP86902794A EP0225338B1 EP 0225338 B1 EP0225338 B1 EP 0225338B1 EP 86902794 A EP86902794 A EP 86902794A EP 86902794 A EP86902794 A EP 86902794A EP 0225338 B1 EP0225338 B1 EP 0225338B1
Authority
EP
European Patent Office
Prior art keywords
pressure
lubricating
pump
outlet
channel
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.)
Expired
Application number
EP86902794A
Other languages
German (de)
English (en)
Other versions
EP0225338A1 (fr
Inventor
Siegfried Hertell
Dieter Otto
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.)
Oerlikon Barmag AG
Original Assignee
Barmag 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 Barmag AG filed Critical Barmag AG
Publication of EP0225338A1 publication Critical patent/EP0225338A1/fr
Application granted granted Critical
Publication of EP0225338B1 publication Critical patent/EP0225338B1/fr
Expired legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the invention relates to an internal combustion engine, the lubricating oil pump of which is a control pump for hydraulic fluid, the flow rate of which is speed-dependent up to a limit value and, moreover, remains essentially constant regardless of the speed.
  • a piston machine is known from DE-OS-2 758 376, the oil pump of which is an internal rotor gear pump. With this pump, the teeth are designed so that a degree of coverage of 1 is aimed for.
  • An internal combustion engine is also required to have a long service life without expert maintenance. This is opposed to the fact that the internal combustion engine is subject to wear, which leads to an increase in lubricating oil consumption and to a drop in pressure in the lubricating oil system.
  • the lubricating oil pump must therefore also be adapted to this increasing demand in the course of the service life. This leads to the fact that this delivery portion of the lubricating oil pump, which is not required, leads to corresponding energy losses.
  • the object of the invention is to provide a lubricating oil system for an internal combustion engine, in which, on the one hand, the lubricating oil pump supplies a sufficient amount of lubricating oil in all operating states, on the other hand, however, unnecessary, lossy delivery is avoided.
  • the toothing is carried out so that the tooth flanks of the teeth, which lie between the intersections of the tip circles, are in engagement with one another and therefore form individual cells in their tooth gaps, which are closed off from one another in the circumferential direction.
  • the engagement of the teeth of the outer wheel and the inner wheel (s) assigned to one another should advantageously begin in the area of the intersection of the tip circles.
  • the tooth mesh does not extend absolutely exactly to the intersection of the tip circles.
  • the invention further provides that the inlet opening of the pump has a throttling effect. This means that the cross-section of the inlet opening is so small or reduced by installing a throttle that only a limited delivery rate can flow through the inlet into the pump for a given pressure drop.
  • an outlet is essentially assigned to each tooth gap which is created by the tooth engagement as a closed cell.
  • Several of these outlets open into a common pressure channel. In this case, separate pressure systems can be fed from the remaining outlet channels. If this is not the case, all outlets open into the common pressure channel. With a few exceptions, all outlets are secured by check valves with flow direction in the outlet direction. The only exception is the tooth cell closest to the intersection of the head circles or possibly the tooth next but one. These tooth cells open into the pressure channel. The distance between the outlets corresponds to the tooth pitch or is smaller than the tooth pitch.
  • valve arrangement is designed in such a way that the cells that arise in the outlet area only open towards the pressure chamber if, due to the progressive compression, the operating pressure of the pressure channel has also been reached in the respective cell.
  • the invention provides a tooth shape which ensures that the tooth flanks of the two toothed wheels located in the pressure region, ie between the intersections of the tip circles, come into such good contact with one another that the two between them Intermeshing flanks formed column can be referred to as hydraulically tight and the pump works silently.
  • the toothing is designed so that the tooth flanks that mesh with each other touch with as large a surface as possible or face each other. Therefore, adjacent tooth cells are sealed from each other by a gap that is as long as possible.
  • the toothing is designed as a cycloid toothing.
  • the cycloid toothing is designed with a curved line of engagement extending from the pitch point to the intersection of the two tip circles.
  • the radius of curvature of the line of engagement preferably assumes values which lie in their dimensions between the pitch circle radius of the inner toothing of the outer wheel and the pitch circle radius of the outer toothing of the inner wheel or wheels.
  • the line of engagement can be a curved line with a constantly changing radius of curvature within the specified limits or lie on a circle, the radius of which is defined within the previously specified limits.
  • the selected toothing has a special shape that falls outside the scope of the known, in that the pitch circles are shifted from the usual position.
  • the distance between the pitch circle and the tip circle, for the external toothing of the inner gear or the distance between the pitch circle and the root circle is significantly smaller than the gear module or the other tooth part.
  • the respectively larger section of the teeth to the smaller section advantageously behaves at least as 2: 1 and preferably as 3.5: 1 to 5: 1.
  • the center of curvature of the line of engagement describes an arc. This means that when the inner wheel is stationary and the outer wheel is rolling, the lines of engagement assigned to the individual teeth of the outer wheel, which are congruent to one another, each lie on an associated circle, the individual center points of the circle lying on a circle concentric with the outer wheel.
  • the invention provides a gear pump which has a delivery and output characteristic that increases with the speed only up to a certain speed. If this speed is exceeded, the rotating cells are only partially filled, and the filling decreases with increasing speed. Adverse consequences of the resulting cavitation and in particular the generally feared cavitation erosion are avoided by the selection according to the invention of only those gear pumps which have cells that are closed relative to one another, and by the design of the outlet area according to the invention with a plurality of outlet openings arranged in the circumferential direction, which are closed by check valves. As a result of this embodiment of the invention, the only partially filled cells only come into connection with the pressurized cells and the pressure chamber when the pressure of the partially filled cell has reached the system pressure. This prevents cavitation explosions.
  • the partial filling of the cells in the inlet area results from the throttling of the inlet channel which is always present there and which allows only a limited inlet oil flow which is not sufficient to completely fill each cell in the filling time specified by the pump speed.
  • throttles adapted to the application and operational purpose of the pump can also be used in the inlet duct.
  • the invention further provides that this throttle is bypassed by a bypass channel and that there is a valve in the bypass channel which is controlled by the outlet pressure of the control pump and which opens the bypass when the pressure in the outlet channel drops.
  • the throttle is set so that the amount of oil that is delivered by the control pump depends on the speed only up to a certain speed.
  • This z. B. taken into account the fact that the lubricating oil consumption of an engine in the lower speed ranges is speed-dependent. On the other hand, it is taken into account that the dependence of the lubricating oil consumption on the speed only exists up to a certain speed.
  • This threshold speed can be specified by dimensioning the throttle.
  • control system can be anyone, e.g. B. Adjust increased additional wear due to wear by determining the pressure drop and using it to open a bypass. By opening the bypass, the entire delivery capacity or an additional portion of the delivery capacity of the control pump can be accessed.
  • the outer wheel 1 is freely rotatably mounted in the housing 31.
  • the outer wheel 1 has an internal toothing 2.
  • the cylindrical housing 31 is closed on both sides by the covers 32 and 33.
  • the shaft 34 is rotatably supported and driven by a motor, not shown.
  • the inner wheel 3 is rotatably mounted on the shaft 34.
  • the inner wheel 3 has an external toothing 4 which is in engagement with the internal toothing 2 of the outer wheel 1.
  • the inlet channel 35 is connected to the tank 36 via a throttle 37.
  • a pressure control valve 39 is located in a bypass 38, which is connected in parallel to the throttle channel 37.
  • the piston 40 of the pressure control valve controls the opening of the bypass channel 38 to the tank 36 with its control edge 41.
  • the piston is on one side with a spring 42 charged.
  • the piston in control chamber 43 is acted upon by the outlet pressure via control line 44.
  • the outlet side of the pump will be discussed later.
  • the function of the pressure control valve 39 as a function of the outlet pressure is described below. As long as there is no or only a low outlet pressure in the control line 44 and the control chamber 43, the piston with its control edge releases the flow from the inlet 45 to the outlet 46.
  • Oil can now flow from the tank 36 to the pump both via the throttle 37 and the bypass channel 38.
  • the pressure in the control chamber 43 rises and the spring force overcomes, the inlet with respect to the outlet 46 is closed. Now only a throttled oil flow flows through the throttle 37 from the tank 36 to the inlet 35 of the pump. If the outlet pressure rises further, the pressure control valve acts as a pressure relief valve. The spring 42 is compressed so far that the front control edge 47 opens the pressure line 44 opposite the outlet 46 to the tank.
  • the pump forms - as shown in FIG. 1 - on the outlet side between the intermeshing teeth of the outer wheel 1 and inner wheel 3, four cells which are closed in the circumferential and axial directions and have been filled with oil via the inlet channel 35.
  • Four outlet kidneys 48.1, 48.2, 48.3, 48.4 are introduced into the cover 32. 2 shows only one of these outlet kidneys. This outlet kidney is designated there by 48.
  • Each of the outlet kidneys is connected to an outlet channel 49 drilled in the cover 33.
  • the outlet channel is also directed radially outwards, as shown in FIG. 2. Therefore, each outer channel 49 opens on the outside of the cover 33 as close as possible to the housing 31.
  • An outlet housing 50 is placed on the cover 33 in a pressure-tight manner.
  • the outlet housing 50 forms an outlet chamber which is connected to the outlet kidneys 48.1 to 48.4 via a pressure channel 49 and a bore 52.
  • the bores 52.1, 52.2 and 52.3 are each closed by a check valve.
  • the check valve is formed by an m-shaped plate which is screwed against the wall 53 of the outlet housing 50.
  • the tongues protruding from the common crossbeam 55 of the check valve 54 cover the bores 52. Therefore, these tongues act as check valves, which only release the connection from the respective pressure cell formed between the teeth, via outlet kidney 48, the respective pressure channel 49 and bore 52, when the pressure of the outlet cell is at least equal to the outlet pressure in the outlet chamber 51.
  • the last and smallest pressure cell is connected directly to the outlet chamber via kidney 48.4 and corresponding channels 49, 52.
  • the outlet chamber 51 has an outlet which leads into the common pressure channel 56.
  • the function of the pump at low pressure in the outlet chamber 51, the spring 42 moves the piston 40 - in FIG. 2 - to the left.
  • the pump now acts like a normal internal gear pump.
  • the oil flow flows through throttle 37 and bypass channel 38 to the inlet. All tooth gaps are filled to the maximum and expressed again on the outlet side. Whether the filling is complete or only partial depends on the throttle resistance of the throttle 37 and the bypass channel 38.
  • the throttle 63 is shown symbolically, which indicates that the bypass 38 also causes throttling, which at high speeds can lead to the fact that the tooth cells are only partially filled. This will be referred to later.
  • the pump is therefore particularly suitable for motor vehicles, in particular as a lubricating oil pump in motor vehicles. If this increases the need for lubricating oil, e.g. B. due to wear, the threshold pressure in the control pressure chamber 43 is only reached at a higher speed. Therefore, the bypass 38 is also closed later. As a result, the lubricating oil pump automatically adapts to an increased demand. The lubricating oil pump therefore meets the increasing need for lubricating oil throughout the life of the motor vehicle engine. On the other hand, the lubricating oil pump works economically even with a new engine with a relatively low need for lubricating oil, since with this lubricating oil pump it is avoided that an unneeded feed portion must be returned to the sump with losses.
  • control pump also meets other requirements of special operating conditions. So it can e.g. B. occur in motor vehicle engines that the lubricating oil heats up extremely or that engine parts must be cooled by lubricating oil due to special performance requirements.
  • a further short-circuit channel 58 is provided between the inlet 35 of the pump and the tank 36.
  • This short-circuit channel is an electromagnetically switched valve 59.
  • This valve is connected via signal line 60 and amplifier 61 z. B. actuated by a temperature sensor 62. Through the temperature sensor z. B. the oil temperature or the temperature of a machine part, for. B. pistons can be detected. It is also possible to use a different measuring instrument, e.g. B.
  • the message line can also be used to record other extraordinary operating conditions.
  • the valve 59 serves the purpose of meeting an extraordinary need. It is assumed here that the sum of the oil flow, which is conveyed by throttle 37 on the one hand and via bypass 38 on the other hand, is still throttled and therefore, despite the pressure control valve 39 being open, only a partial filling of the cells of the internal toothing takes place at speeds that exceed a certain threshold speed lie. Fig. 2 meets this requirement in that a further throttle 63 is indicated in the bypass 38.
  • Fig. 3 serves to explain the toothing, which is preferably used in the context of this invention.
  • the outer wheel 1 has an internal toothing 2, in which the inner wheel 3 meshes with its external toothing 4. Compared to the fixed outer gear 1, the inner wheel 3 rotating in the direction of arrow 24 moves in the direction of arrow 23.
  • the pitch circle 7 of the outer wheel like the pitch circle 8 of the inner wheel 3, is oriented in the direction of the tooth height 14 and the center points 17 and 25 of the pitch circles the center points 17 and 25 shifted, whereby a small section 16 of the teeth 2 and 4 and a much larger section 15 are formed, both of which complement each other to the tooth height 14 which is practically the same for both wheels 1 and 3.
  • the distance between pitch circle 7 and root circle 6 of outer wheel 1 and between pitch circle 8 and tip circle 9 of inner wheel 3 is preferably at least twice the distance between pitch circle 7 and tip circle 5 for outer wheel 1 or the distance between pitch circle 8 and the base circle 10 of the inner wheel, the ratio of the dimensions between the two tooth sections 15 and 16 preferably having a value between 3.5: 1 and 5: 1.
  • the line of engagement 11 extending through the pitch point 12 and the intersection 13 of the tip circles 5 and 9 lies on a circle with the radius 26 which starts from the center point 19 of the circle. If the inner wheel rolls on the stationary ring gear, the center of curvature 19 describes a circle 18 which is concentric with the pitch circle 7 of the outer wheel. The straight line 21 between the center of the ring gear 17 and the respective pitch point 12 intersects this circle at the current center of curvature. The radius of the circle 18 is determined by the specified conditions. The resulting form of gearing solves the task in an outstanding manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

Une pompe à capacité variable hydraulique conçue comme pompe à roue dentée intérieure, dans laquelle les dents de la roue extérieure (1) et de la roue intérieure (5) sont engagées les unes avec les autres entre les points d'intersection des cercles de tête de la denture. Ainsi des cellules de denture sont créées dans la région de sortie. Les cellules de la denture débouchent dans un canal de sortie commun à toutes, par des canaux de sortie (48) qui sont disposés à une certaine distance de la denture et qui sont fermés à chaque fois par une soupape de retenue. L'entrée est reliée au réservoir par deux ou trois canaux, dont le premier est équipé d'un papillon fixe (37), le deuxième est commandé par une soupape de commande de la pression (39) agissant en fonction de la pression régnant dans le chambre de compression (51) et le troisième est commandé par une soupape électromagnétique (59) agissant en fonction d'autres paramètres de fonctionnement.

Claims (3)

1. Moteur à combustion comportant une pompe à huile de lubrification et un canal d'huile de lubrification (56), caractérisé en ce que la pompe à huile de lubrification est une pompe à engrenages internes dans laquelle la denture est réalisée de telle sorte que les flancs des dents sont en contact pour l'essentiel pour toutes les dents qui se trouvent entre les points d'intersection (13) des cercles de tête (5, 9) et forment des cellules de sortie qui sont étanches les unes par rapport aux autres du point de vue hydraulique, au moins les cellules de sortie présentant un volume plus important étant fermées par rapport au canal d'huile de lubrification (56) par un clapet antiretour (54) et en ce que dans le canal d'aspiration (35) de la pompe à huile de lubrification se trouve une restriction constante (37) qui est contournée par un canal à bypass (38) comportant une valve commandée par pression (39) lorsque la pression dans le canal de sortie est inférieure à une valeur de seuil.
2. Moteur à combustion selon la revendication 1, caractérisé en ce que la valve commandée par pression (39) présente une chambre de commande par pression (43) qui, en cas de dépassement d'une pression maximale admissible, ouvre vers la bâche (36).
3. Moteur à combustion selon la revendication 1 ou 2, caractérisé en ce que l'entrée (35) de la pompe à huile de lubrification est reliée à un canal d'entrée (58) qui ne présente pas de restriction et peut être ouvert ou fermé par une valve électromagnétique (59) afin de couvrir un besoin particulièrement important en huile de lubrification.
EP86902794A 1985-05-09 1986-05-06 Pompe a capacite variable Expired EP0225338B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3516718 1985-05-09
DE3516718 1985-05-09

Publications (2)

Publication Number Publication Date
EP0225338A1 EP0225338A1 (fr) 1987-06-16
EP0225338B1 true EP0225338B1 (fr) 1989-10-25

Family

ID=6270274

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86902794A Expired EP0225338B1 (fr) 1985-05-09 1986-05-06 Pompe a capacite variable

Country Status (5)

Country Link
US (1) US4750867A (fr)
EP (1) EP0225338B1 (fr)
JP (1) JP2598396B2 (fr)
DE (1) DE3666606D1 (fr)
WO (1) WO1986006797A2 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3716083A1 (de) * 1987-05-14 1988-11-24 Kuehnle Kopp Kausch Ag Innenachsige drehkolbenmaschine
DE3824398C2 (de) * 1987-07-23 1993-11-18 Barmag Barmer Maschf Schmierölpumpe
DE3933978A1 (de) * 1989-10-11 1991-05-02 Eisenmann Siegfried A Sauggeregelte zahnringpumpe
CH684965A5 (de) * 1991-10-18 1995-02-15 Linde Ag Verfahren und Vorrichtung zur Erhöhung des Wirkungsgrades von Kompressionsvorrichtungen.
EP0619430B1 (fr) * 1993-03-05 1997-07-23 Siegfried A. Dipl.-Ing. Eisenmann Pompe à engrenage internes pour gamme de vitesses rotatives élévées
EP0845080B1 (fr) * 1995-08-14 2000-11-22 Stackpole Limited Regulation de la pression de sortie pour pompe a engrenage interieur
US5722815A (en) * 1995-08-14 1998-03-03 Stackpole Limited Three stage self regulating gerotor pump
DE19625564C2 (de) * 1996-06-26 2000-06-08 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen
AT407563B (de) * 1998-02-26 2001-04-25 Tcg Unitech Ag Ölpumpe für eine brennkraftmaschine mit innerer verbrennung
JP4928447B2 (ja) * 2004-06-24 2012-05-09 ルーク アウトモービルテヒニーク ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディトゲゼルシャフト ポンプ
CN100337048C (zh) * 2005-12-05 2007-09-12 关跃 泵式液压偶合器

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DE409134C (de) * 1924-01-22 1925-02-02 Bbc Brown Boveri & Cie Verdichter oder Expansionskraftmaschine nach Art einer Zahnradpumpe
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DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
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Also Published As

Publication number Publication date
DE3666606D1 (en) 1989-11-30
JPS63500112A (ja) 1988-01-14
EP0225338A1 (fr) 1987-06-16
JP2598396B2 (ja) 1997-04-09
WO1986006797A2 (fr) 1986-11-20
US4750867A (en) 1988-06-14

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