DE19523533C2 - Suction-controlled internal gear pump - Google Patents

Suction-controlled internal gear pump

Info

Publication number
DE19523533C2
DE19523533C2 DE1995123533 DE19523533A DE19523533C2 DE 19523533 C2 DE19523533 C2 DE 19523533C2 DE 1995123533 DE1995123533 DE 1995123533 DE 19523533 A DE19523533 A DE 19523533A DE 19523533 C2 DE19523533 C2 DE 19523533C2
Authority
DE
Germany
Prior art keywords
working fluid
channel
internal gear
gear pump
pressure
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 - Fee Related
Application number
DE1995123533
Other languages
German (de)
Other versions
DE19523533A1 (en
Inventor
Siegfried A Dipl Ing Eisenmann
Original Assignee
Eisenmann Siegfried A
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 Eisenmann Siegfried A filed Critical Eisenmann Siegfried A
Priority to DE1995123533 priority Critical patent/DE19523533C2/en
Priority claimed from CA 2159672 external-priority patent/CA2159672C/en
Priority claimed from DE1995508170 external-priority patent/DE59508170D1/en
Publication of DE19523533A1 publication Critical patent/DE19523533A1/en
Application granted granted Critical
Publication of DE19523533C2 publication Critical patent/DE19523533C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • F04C14/10Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C14/12Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • 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
    • F04C14/24Control 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

Description

The present invention relates to an internal gear pump in the preamble of claim 1 designated genus.

Such pumps are e.g. B. known from DE 39 33 978 A1. Of the As a rule, it is driven by the shaft carrying the pinion le. The delivery target of such pumps, e.g. B. the lubrication pump one Motor vehicle engine is only in the lower part of the operating range proportional to the speed. The increases in the upper speed range Lubricant and working fluid requirements are much lower than the speed of the engine. So that a suction control Pump necessary.

The disadvantage of such a suction control is that which occurs Cavitation. The one to be expected by increasing the speed linear pressure rise cannot in the pressure range of such pumps are held, rather the pressure increases from a certain one Speed not linear with a lower gradient. In the sub the full geometric delivery rate in the working area cavitation occurs well above the proportionality range, which leads to implosions of the gaseous components of the cell contents, so that undesirable noises and damage to the cell walls are the result. Furthermore  such pumps have relatively low effectiveness in higher speed ranges straight up.

US 3,272,128 describes a reversible hydraulic pump with a variable Volume of the inside-outside gear type. The control of the volume flows in this Pump is to be carried out from the outside via a control shaft. The pump has two levels with kidney and supply channels, namely above and below the pinion. she can be used and designed for two directions of rotation.

Such a pump is not self-regulating and solves for the volume flows also does not address the cavitation and Efficiency.

The above also applies to the gear pump described in DE 29 33 493 A1 with a Bypass channel routing, especially with regard to self-control.

It is the object of the present invention to provide an internal gear pump to make, which no longer the disadvantages of the prior art mentioned above points. In particular, an internal gear pump with minimal cavitation and high Efficiency can be provided that ver the volume flows a self-control really.

This task is solved by an internal gear pump, which mark according to the the part of claim 1 is designed.

Preferred embodiments are described by the subclaims.

The decisive advantage of this new internal gear pump is that regulated supply of working fluid from the outlet mouth into an inlet mouth and the simultaneous interruption of the supply of working fluid from the inlet duct in this inlet mouth, a delivery cell, in which pressure increases with increasing speed waste and thus cavitation would occur on the higher  Outlet pressure is brought. This will cause cavitation in this Delivery cell avoided. There is also a great advantage in that because no cavity, i.e. H. no negative pressure in the This conveyor cell is created, but pressurized it this pressure generates a positive torque on the pinion. This feed cell, which is under higher pressure, is working thus like a hydraulic motor, which makes it very efficient can be reached.

According to a preferred embodiment which connects in the kenn drawing part of claim 1 called device at stei pressure in the pressure area one after the other orifice with the pressure area. This will help increasing speed ensures that that För cell in which pressure drop and thus cavitation occur could be pressurized in time so that Noise and damage can be avoided.

Advantageously, the device that characterize the part of claim 1 is described, one with the The outlet port is connected to the transition channel, which has a Valve device opens into at least one supply channel, wel cher in turn is connected to an inlet mouth. The Valve device can thus regulate the supply of work liquid from the outlet mouth, i.e. the pressure area, in control the inlet mouth and at the same time the supply of Ar liquid from the inlet channel into this inlet mouth first throttle and later interrupt. To this end, a such valve device preferably has a valve piston, against the pressure by means of a spring supported in the housing of the working fluid stored in the transfer channel is and by means of a head heel access to the work flow locks or releases liquid into the feed channels. The feather offers a different choice of stiffness Possibility to control the operating behavior of the valve direction, while the head of the valve piston is so trained Det can be that the pressurized working fluid  presses against one of its surfaces against the spring force, while with its side surfaces it feed channels for the Working fluid locks depending on the position of the valve piston or releases.

The valve piston can be in the depressurized state of the transfer valve nals or up to a predetermined pressure in this against the Force of the spring by a stop on the housing in one position be kept where no working fluid from the over entry channel flows into a supply channel. This state ent speaks the initial position of the valve device at lower Speed or when the pump is at a standstill. The opposite The attachment point of the valve piston can be determined by that the valve piston is in the position where working fluid is out the transfer channel flows into all feed channels, in his Movement against the direction of the spring force is stopped, because the spring is blocked.

The inlet mouth for those not connected to the transfer duct connecting conveyor cells is preferably about in size limits the area in which these production cells extend. This ensures that those Förderzel len, with increasing speed with pressure from the high pressure space to be acted upon, completely removed from the suction space can be cut. In contrast, the outlet port approximately over the entire area of the production cells ken, which is downstream of the conveyor cells lie, which can be connected to the transition channel. This design of the outlet mouth is suitable because the related promotional cells practical be under high pressure during the entire operation.

In a preferred embodiment, this forms the head heel opposite end of the valve piston together with the housing one Spring chamber working to dampen the piston movement liquid is filled and through a hole in liquid is connected to the working fluid in the inlet duct.  

The valve device advantageously acts simultaneously as Safety valve in the form of a bypass valve. If at Höchst print the last feed channel in the print area of the head heel has exceeded so far that under decompression a short circuit flow of the working fluid from the pressure area therefore occurs only in the inlet channel, the spring then goes on block if a sufficient discharge cross-section is created is.

In a further advantageous embodiment of the The invention has the pinion of the internal gear pump two Teeth less than the gear ring, and in the place of Au The engagement of the teeth is a crescent-shaped skin fixed filler provided. The teeth of the Toothed ring be made sufficiently pointed, so that in the Saugbe reach the conveyor cells against each other via the tooth mesh are sealed.

Furthermore, the internal gear pump according to the invention can thereby be characterized in that the head of the valve piston a sales base and a lengthways adjoining this set flag with the same outer diameter, the Guide and the sealing function of the valve piston in the housing bore on the housing heels on the outer surfaces of the heel base and the sales flag.

The invention will now be described with reference to the accompanying Drawings described in more detail. Show it:

Fig. 1 is a cross-sectional view of a gear pump according to the invention, in which the position of the Ventilein direction is shown in the start-up state of the pump;

Fig. 2 is a cross-sectional view of the internal gear pump according to the invention in a state with increased speed compared to Figure 1;

Fig. 3 is a cross-sectional view of the internal gear pump according to the invention, the speed has risen so far that the valve device already releases a feed cell separated from the feed through its inlet mouth for pressurizing from the pressure area;

Fig. 4 is a cross-sectional view of the internal gear pump according to the invention, in which the valve device has assumed a position in which all inlet openings and supply channels supply the feed cells connected to them with high-pressure working liquid; and

Fig. 5 shows a further embodiment of the internal gear pump according to the invention, wherein the pinion has two teeth less geri than the toothed ring and at the point of disengagement of the teeth a crescent-shaped, housing-fixed filler is provided.

In Fig. 1 a cross-sectional view of an execution form is shown an internal gear pump according to the invention. The pump has a housing 1 which encloses a gear chamber 6 with a toothed ring 2 . With the toothed ring 2 meshes a Rit zel 3 , which has one tooth less than the toothed ring 2nd The pinion 3 forms with the toothed ring 2 successive feed cells 10 , 11 , 12 , 13 , 14 , 15 and 16 that seal against one another by the tooth engagement. An inlet channel 4 opens into an inlet mouth 7 formed as an inlet kidney, which is shown in dashed lines. Furthermore, the inlet channel 4 in the position shown in FIG. 1 is connected via a housing bore 17 with housing shoulders 17 a, 17 b, 17 c and 17 d to the supply channels 22 a, 22 b and 22 c, which into the inlet openings 8 a, 8 b and 8 c expire.

On the outlet side, the housing has an outlet 5 which is connected to the gear chamber disposed in the outlet kidney 6 9, which is also shown in dashed lines. Wei ter is the outlet kidney 9 on its side facing the outlet mouth 5 abge connected to a transition channel 20 , which tion on the opposite side of the inlet channel 4 side of the housing bore 17 at the housing shoulder 17 a opens into this. A valve device is provided on the lower part of the housing 1 . A valve piston 21 is in this position of the valve device in the housing bore 17 , a shoulder 24 of this valve piston 21 strikes with its front end in the passage channel 20 against the housing and with its side surfaces, the housing bore 17 on the housing shoulder 17 a against the liquid seals in the transfer channel 20 . At its rear end, the valve piston 21 is guided with its rear set 29 in a spring chamber 25 , in which in a spring 23 in the direction of the attachment point on the housing (in the left direction in Fig. 1) against the pressure in the transfer channel 20 or against stops the head paragraph 24 on the housing 1 . The spring chamber is tightly closed at its right end with a locking screw not shown. A bore 26 in the valve piston 21 connects its surroundings with the spring chamber 25 filled with working fluid, whereby a damping effect occurs.

Starting from this Fig. 1 designating all components, the operation of the internal gear pump according to the invention will now be described with the help of the other figures. The same construction parts are provided with corresponding reference numerals in all figures. In FIGS. 2 to 5, however, the clarity sake be no longer refers to all, but only the relevant components.

In the state shown in Fig. 1, the pinion 3 is rotated in the direction indicated by the arrow n. Liquid is sucked in via the inlet channel 4 and, on the one hand, fed to the feed cells 10 and 11 via the inlet kidney 7 . On the other hand, working fluid is also supplied via the housing bore 17 in the space between the valve piston 21 and this housing bore to the supply channels 22 a, 22 b and 22 c and via these the inlet ports 8 a, 8 b and 8 c, which feed cells 12 and 13 supply with working fluid. In the state shown in Fig. 1, the pump in the proportional range, ie the flow increases linearly with an increase in speed n. Since the head shoulder 24 seals the housing bore 17 on the housing shoulder 17 a against the liquid in the transfer duct 20 , only the delivery cells 14 , 15 and 16 are under pressure. The spring force F0 exerts a greater or equal pressure on the valve piston 21 as the pressure P 0 against the surface of the head heel 24 labeled AK.

In the following functional description it is assumed that a consumer is connected to the outlet channel 5 , the hydraulic resistance

 is about constant.

The regulation begins when the force exerted by the working fluid in the transfer channel 20 on the head heel 24 becomes greater than the spring force. In FIG. 2, the pinion 3 rotates with the rotation speed n 1, which is already higher than the limit speed in the proportional band of the pump. The pressure of the working fluid in the pressure range would increase linearly to a pressure P 1 , so that the valve piston 21 is moved to the right. As a result, the suction angle α s is reduced from α s max (see FIG. 1) to α s1 (see FIG. 2). However, the pressure P 1 ″ that could be achieved linearly cannot persist, but drops to P 1 . This means that the flow rate also drops linearly. At the increased speed n 1, a new delivery rate and a new pressure P 1 occur which is lower than P 1 ' but higher than P 0 . The setting of a pressure P 1 , which is higher than the pressure P 0 , is also structurally dependent on the design of the valve device and the pump. If this pressure were not higher than P 0 ' , the valve piston 21 would be pushed back into the original position ( FIG. 1) by the spring 23 , and the process would start again because the speed is increased compared to the starting position. Had the pressure P 1 remained in the pressure range at the value P 1 ', the throttling effect of the piston 21 moving to the right would have remained ineffective due to the head shoulder 24 penetrating into the feed channel 22 a on the filling of the feed cell 12 . Thus, the pressure P 1 must be between P 0 and P 1 '.

A summary of FIGS. 2 and 3 shows what happens when the speed is increased further, here to the speed n 2 in FIG. 3. The process described above for increasing the speed continues, so that the valve piston 21 is pushed ever further to the right by the pressure increase until, as shown in FIG. 3, a state is reached, for example, where the valve piston 21 with its head shoulder 24 seals the housing bore 17 on the housing shoulder 17 c, so that the feed cell designated here 12 is not provided via the inlet duct 4 with the working fluid sucked in, but via the transfer duct 20 and the ducts 22 a and 8 a with the working fluid under pressure. The working fluid in the feed cell 12 is with the downstream feed cells at the increased pressure P 2 , so that no cavity is formed in it and no negative pressure can develop despite the increase in space. On the contrary, this delivery cell 12 generates a positive torque on the pinion 3 due to the pressurization with the pressure P 2 , because its space expands under high pressure and works like a hydraulic motor. This internal differential control thus works with high efficiency. The working fluid under pressure P 2 is not decompressed to atmospheric pressure, but instead returns its potential energy as mechanical power to the pump drive shaft with a certain loss of flow through the channels. The suction angle in this position is designated α s2 .

In the state shown in Fig. 4, the speed n 3 is now increased so far that the valve piston 21 has moved so far to the right that it seals the entire housing bore 17 with its head shoulder 24 against the working fluid in the inlet channel 4 on the housing shoulder 17 d. The designated 12 Förderkam mer and all of her from downstream delivery chambers are now either through the outlet kidney 9 or via the transfer channel 20 and the intersecting supply and inlet channels 22 a, 22 b, 8 a and 8 b with pressurized Working fluid supplied. The spring 23 is pressed onto the block. Half of the feed cells used in the initial stage for suction are separated from the inlet channel 4 and at the same time connected to the high pressure P 3 , so that they act as a hydromotor, as described above. Above all, the pump works practically without cavitation in the entire regulated area, so that no noise is generated. In the speed range from N 0 to N 3 , no aperture or other throttle is necessary in the inlet duct 4 because of the internal control just described.

Is, as in Fig. 4, the valve piston 21 pressed down to the spring block to the right, no further internal control can take place. With further speed increases, the delivery rate with reduced steepness will continue to increase proportionally to the speed until 7 cavitation occurs in the remaining remaining suction tooth chambers in the region of the short suction kidney.

The pump described above is mainly suitable for supplying automatic transmissions with a pressure level up to 25 bar or higher. The rigidity of the spring 23 determines the steepness of the conveyor line in the regulated area and must be adapted to the hydraulic resistance of the consumer.

FIG. 5 shows a further embodiment of the modern fiction, internal gear pump in which two further aspects of the present invention emerge. A first aspect relates to the design of the pump with a pinion 3 , which has two teeth less than the toothed ring 2 .

At the point where the teeth of the pinion 3 come out of engagement with the toothed ring 2 , a crescent-shaped, housing-fixed filler 27 is provided here. The teeth 28 of the toothed ring 2 are designed to be sufficiently pointed in order to sufficiently seal the feed cells for the tooth engagement from one another in the suction area.

The operation of the internal gear pump shown in FIG. 5 and the function of the valve device correspond to those described in FIGS. 1 to 4.

Another aspect of the invention, which becomes clear with reference to FIG. 5, relates to the safety valve action of the valve device. This works as a bypass valve when at maximum pressure in the pressure area of the head attachment 24 has exceeded the last feed channel 22 c to such an extent that short circuit from the pressure area into the inlet channel 4 occurs under decompression. The spring 23 may only go to block when a sufficient outflow cross-section is sufficient at this point. For the function of the valve piston 21 as a safety-valve of the head restraint 24 must be longer than the width of the recess 30th In Fig. 5 the head extension 24 is designed accordingly. If the base of the head is too short, the piston loses its lead.

As further shown in Fig. 5, the head shoulder 24 of the valve piston 21 here consists of a heel base 24 a and a longitudinally adjoining heel tab 24 b with the same outer diameter. The leadership and sealing function of the valve piston 21 in the housing bore 17 on the housing heels take place on the outer surfaces of the heel base 24 a and the heel flag 24 b. Although the heel base 24 a itself is narrow, in particular narrower than the width of the feed channels 22 , good routing and sealing can be ensured by the milled heel tab 24 b.

Claims (10)

1. Internal gear pump with
  • a) a housing ( 1 ) with a gear chamber ( 6 ),
  • b) a toothed ring ( 2 ) in the housing ( 1 ),
  • c) arranged in the toothed ring ( 2 ), with this meshing pinion ( 3 ), which has at least one tooth less than the toothed ring ( 2 ) and with these together successive mutually sealing against each other by the tooth engagement sealing cells ( 10 , 11 , 12 , 13th , 14 , 15 , 16 ) for the working fluid speed, and
  • d) at least one inlet channel ( 4 ) and at least one outlet channel ( 5 ) for the working fluid in the housing ( 1 ),
  • e) wherein the working fluid from the inlet channel via inlet mouths ( 7 , 8 a, 8 b, 8 c) is fed into the suction area of the gear chamber ( 6 ) and via at least one outlet mouth ( 9 ) from the pressure area of the gear chamber ( 6 ) in the Outlet channel ( 5 ) is discharged,
marked by
  • a) a device ( 20 , 21 , 22 ) which, with increasing pressure in the pressure area, supplies a controlled amount of the working fluid from the outlet mouth ( 9 ) into at least one inlet mouth ( 8 a, 8 b, 8 c) while at the same time the The supply of working fluid from the inlet channel ( 4 ) into this inlet mouth ( 8 a, 8 b, 8 c) is interrupted, connecting the inlet mouths ( 8 a, 8 b, 8 c) adjacent to the pressure area one after the other, and thereby, that
  • b) the device ( 20 , 21 , 22 ) has a transfer channel ( 20 ) connected to the outlet mouth ( 9 ), which via a valve device ( 21 , 22 , 23 ) into at least one supply channel ( 22 a, 22 b, 22 c) opens, which in turn is connected to an inlet opening ( 8 a, 8 b, 8 c), the valve device ( 21 , 23 , 24 ) having a valve piston ( 21 ) which is supported by a spring () supported in the housing ( 1 ) 23 ) is mounted against the pressure of the working fluid in the transfer channel ( 20 ) and by means of a head heel ( 24 ) blocks or releases the access of the working fluid into the supply channels ( 22 a, 22 b, 22 c).
2. Internal gear pump according to claim 1, characterized in that the valve piston ( 21 ) in the depressurized state of the transfer channel ( 20 ), or up to a predetermined pressure therein, against the force of the spring ( 23 ) by a stop on the housing ( 1 ) is held in a position where no working fluid flows from the transfer channel ( 20 ) into a supply channel ( 22 ).
3. Internal gear pump according to one of claims 1 or 2, characterized in that the valve piston ( 21 ) in the position where working fluid flows from the transfer channel ( 20 ) into all supply channels ( 22 ), thereby moving against the direction of the spring force is stopped that the spring ( 23 ) is pressed onto the block.
4. Internal gear pump according to one of claims 1 to 3, characterized in that the inlet mouth ( 7 ) for the not to be connected to the transfer channel ( 20 ) conveyor cells ( 10 , 11 ) is limited in size to approximately the area in which these conveyor cells extend.
5. Internal gear pump according to one of claims 1 to 4, characterized in that the outlet mouth ( 9 ) extends approximately over the entire area of the conveyor cells ( 14 , 15 , 16 ), which is downstream in the conveying direction of the conveyor cells ( 12 , 13 ) lie, which can be connected to the transfer channel ( 20 ).
6. Internal gear pump according to one of claims 1 to 5 , characterized in that the head shoulder ( 24 ) facing away from the end of the valve piston ( 21 ) together with the housing ( 1 ) forms a spring chamber ( 25 ) which is used to dampen the piston movement with working fluid is filled and is in fluid communication with the working fluid in the inlet channel ( 4 ) via a bore ( 26 ).
7. Internal gear pump according to one of claims 1 to 6, characterized in that the valve device ( 21 , 23 , 24 ) acts simultaneously as a safety valve in the form of a bypass valve when the top supply ( 24 ) the last supply channel (at maximum pressure in the pressure range) 22 c) has exceeded that under decompression a short-circuit flow of the working fluid from the pressure area into the inlet channel ( 4 ) occurs.
8. Internal gear pump according to one of claims 1 to 7, characterized in that the pinion ( 3 ) has two teeth less than the toothed ring ( 2 ) and a crescent-shaped, housing-fixed filler is provided at the point of disengagement of the teeth .
9. Internal gear pump according to claim 8, characterized in that the teeth of the toothed ring are made sufficiently pointed, so that in the suction area the delivery cells ( 10 , 11 , 12 ) are sealed against each other via the tooth engagement.
10. Internal gear pump according to one of claims 1 to 9, characterized in that the head shoulder ( 24 ) of the valve piston ( 21 ) from a set base ( 24 a) and a longitudinally adjoining this shoulder vane ( 24 b) with the same outer diameter, the guidance and sealing function of the valve piston ( 21 ) in the housing bore ( 17 ) on the housing shoulders ( 17 a, 17 b, 17 c, 17 d) on the outer surfaces of the heel base ( 24 a) and the heel tab ( 24 b) occur.
DE1995123533 1995-06-28 1995-06-28 Suction-controlled internal gear pump Expired - Fee Related DE19523533C2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE1995123533 DE19523533C2 (en) 1995-06-28 1995-06-28 Suction-controlled internal gear pump

Applications Claiming Priority (13)

Application Number Priority Date Filing Date Title
DE1995123533 DE19523533C2 (en) 1995-06-28 1995-06-28 Suction-controlled internal gear pump
CA 2159672 CA2159672C (en) 1994-10-17 1995-10-02 A valve train with suction-controlled ring gear/internal gear pump
DE1995508170 DE59508170D1 (en) 1994-10-17 1995-10-10 Suction-controlled gear ring / internal gear pump
ES95115966T ES2146694T3 (en) 1994-10-17 1995-10-10 Internal gear pump with regulated suction.
EP95115966A EP0712997B1 (en) 1994-10-17 1995-10-10 Suction regulated internal gear pump
KR1019950035270A KR960014598A (en) 1994-10-17 1995-10-13 Valve train and gear pump
CN 95116181 CN1131731A (en) 1994-10-17 1995-10-16 Valve train with suction-controlled ring gear/internal gear pump
JP26889595A JP2825782B2 (en) 1994-10-17 1995-10-17 Valve train with suction control ring gear / internal gear pump
US08/544,074 US5738501A (en) 1994-10-17 1995-10-17 Internal gear pump
BR9504427A BR9504427A (en) 1994-10-17 1995-10-17 Valve set for internal combustion engine and internal gear pump
ARP960103342A AR004173A1 (en) 1995-06-28 1996-06-27 Pump idler
US08/969,055 US5842449A (en) 1994-10-17 1997-11-12 Valve train with suction-controlled ring gear/internal gear pump
JP6176098A JP3292458B2 (en) 1994-10-17 1998-03-12 Valve train with suction control ring gear / internal gear pump

Publications (2)

Publication Number Publication Date
DE19523533A1 DE19523533A1 (en) 1997-01-02
DE19523533C2 true DE19523533C2 (en) 1998-06-18

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
DE1995123533 Expired - Fee Related DE19523533C2 (en) 1995-06-28 1995-06-28 Suction-controlled internal gear pump

Country Status (2)

Country Link
AR (1) AR004173A1 (en)
DE (1) DE19523533C2 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11280667A (en) * 1998-03-27 1999-10-15 Aisin Seiki Co Ltd Oil pump device
DE102005030251B4 (en) * 2005-06-29 2017-03-23 Bayerische Motoren Werke Aktiengesellschaft Gear pump, in particular gear oil pump for vehicles
DE102005032644B4 (en) 2005-07-13 2018-06-21 Bayerische Motoren Werke Aktiengesellschaft Gear pump, in particular gear oil pump for vehicles
DE102006025367B4 (en) * 2006-06-01 2014-09-04 Bayerische Motoren Werke Aktiengesellschaft Gear pump, in particular gear oil pump for vehicles
DE102010019933A1 (en) * 2010-05-08 2011-11-10 Volkswagen Ag Method for operating an internal combustion engine with a multistage oil pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3272128A (en) * 1964-06-15 1966-09-13 Emerson Electric Co Variable volume reversible hydraulic device
DE2933493A1 (en) * 1979-08-18 1981-03-26 Daimler Benz Ag High temperature hydraulic gear pump - has oil entraining and release galleries formed in housing adjacent two meshing gears
DE3933978A1 (en) * 1989-10-11 1991-05-02 Eisenmann Siegfried A Suction-controlled gear ring pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3272128A (en) * 1964-06-15 1966-09-13 Emerson Electric Co Variable volume reversible hydraulic device
DE2933493A1 (en) * 1979-08-18 1981-03-26 Daimler Benz Ag High temperature hydraulic gear pump - has oil entraining and release galleries formed in housing adjacent two meshing gears
DE3933978A1 (en) * 1989-10-11 1991-05-02 Eisenmann Siegfried A Suction-controlled gear ring pump

Also Published As

Publication number Publication date
AR004173A1 (en) 1998-11-04
DE19523533A1 (en) 1997-01-02

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