MXPA97009436A - Infinated regulation gear pump infin - Google Patents

Abstract

The present invention relates to an annular gear pump of infinite regulation, comprising: a stationary cover, an internal rotor (3) on the cover, rotatably supported and driven by means of an axis (2), and an external rotor ( 4) in the same way supported in a rotating manner, coupled with said internal rotor (3), formed the set of ring gears by an external tooth of the internal rotor and an internal tooth of the external rotor, the difference being in the number of teeth of the game of annular gears (5), being equal to the unit, presenting a tooth shape in which a plurality of expansion and contraction displacement cells (7), each sealed with respect to the other, conform due to the point contact between teeth, and the adjusting gear (20; 21) being formed by an external toothing (24; 22: 52; 100) in an adjusting ring (14) and an internal toothing (24 '; 23; 53; 103) of the cover, the external toothing (24; 22; 52; 100), coupling with the The internal toothing (24 '; 23; 53; 103), and provided in the cover openings (8,9) of low pressure and high pressure in the form of kidney, fixedly arranged and laterally in the region of said cells displacement (7), the openings being separated from one another by means of partitions (10, 11), and the angular position of the eccentric axis (eccentricity 17) of the ring gear set (5), is variable to the cover, where the support (12) of the external rotor (4), of the ring gear set (5), is produced in the outer diameter (13) of the latter in an adjusting ring (14), which preferably has the same width, the gear of adjustment (20; 21) is configured as a complete or partial internal gear (24, 24 ', 22, 23,; 52, 53; 100, 103) having the same eccentricity (17) as said ring gear set (5) , by means of which, the adjusting ring (14) is rolling with a zero displacement by its external circle or step circle (15), on a circle internal or circle of passage (16) of the cover, the difference in the diameters of the two circles or circles of passage (15, 16) is equal to twice that of eccentricity (17), of the ring gear set (

Description

The present invention relates to an infinitely variable annular gear pump, comprising a stationary tire, an inner rotor in the tire that is rotatably supported and driven by means of an axle and an external rotor which is in the same way rotatably supported and which meshes with the internal rotor, the difference in the number of teeth of the ring gear set comprising the inner rotor and the outer rotor is equal to the unit, including a tooth shape in which a plurality of expansion and The shrinkage are each sealed with respect to the other which is materialized due to the point contact between teeth and the high and low pressure ports in the form of a kidney which are fixedly arranged laterally in the region of the displacement cells provided in the cover, the ports being separated from each other by partitions and the angular position of the eccentric shaft (ex center) of the ring gear set is variable with respect to the cover, wherein the support or support of the outer rotor of the annular gear set is produced in an outer diameter of the latter in an adjusting ring which preferably has the same width and which rolls with zero slip through its pitch circle or outside differential circle on a pitch circle or inner circumferential circle and the difference in the diameters of the two pitch circles is equal to twice the eccentricity of the annulus set. The specific supply (displacement / speed) of the variable annular gear pump according to the invention can be modified. The known gear pumps provide a specific supply that is constant due to the system involved, since the geometry of the displacement "cells" can not be varied. The expansion and contraction displacement cells fluctuate during rotation of the gear set from a minimum to a maximum and back again to a minimum, because the teeth are rigid and non-variable. This constant in the specific supply automatically results in a supply of the pump that is proportional to its speed of rotation as long as the displacement cells are 100% full. However, in many applications this proportionality is not desirable and is detrimental. Although in a press, for example, a high supply of hydraulic fluid is required for rapid advancement, so that in the final phase of the working stroke only high pressure is supplied, the hydraulic fluid supply requirement falls to zero. Since the driving speed of such pumps remains a constant rule, the excess supply materializes in the high pressure that is returned to the fluid container with a loss of energy. This excess supply is particularly detrimental, for example, in the case of motor lubrication pumps, for vehicle engines, and in the case of oil supply pumps in automatic transmissions. Although these require at a lower engine speed and therefore at lower pump speeds a minimum supply needed for idle operation and minimal oil pressure at high speeds, the required lubricant flow at high speeds is below the line of proportionality, and yet, it is mostly less than one third of the flow of proportionality at maximum speeds. In spite of the many efforts made to solve this problem by acceleration by suction, solutions have been proposed that involve pumps of the variable vain type. Also known are solutions that used two-register pumps to achieve at least two stages of supply or involve two operating sets that operate in a variable manner with respect to each other. A good approach to solve the problem is the provision of an annular gear pump since an internal gear pump does not require an increase because the shape of the gear is selected such that by means of the point contact between teeth each tooth chamber is reliably sealed with respect to to the adjacent dental chambers in order to achieve a good volumetric efficiency. In such annular gear pumps there is the possibility to vary the axial spacing of the inner rotor with respect to the external rotor or the angular location of the eccentric shaft with respect to the cover and thus with respect to the ports and openings of supply and discharge in the cover. A design solution could consist of the support or support of the external rotor in a cam ring rotatably disposed in a variable manner in the cover. For a near zero adjustment of supply needed in practical applications, as in the case of a cold start, where it is highly desired, an angular adjustment of 90 ° of the cam or eccentric shaft is necessary. This means that the cam ring to adjust the eccentric axis of the play of the operation needs to be rotated through 90 ° and thus along a large perimeter, this in turn requiring a very large displacement of the drive spring that could give as a result dimensions that are very difficult to achieve due to the necessary soft spring characteristic. Since, especially in the case of vehicle engines and in the case of automatic transmissions, very frequent and rapid changes in speed occur, the cam ring should experience high rotational accelerations and delays that could result in high set-up forces. resistance to them and high wear. Also, the risk of dirt and particles in large regulation spaces is high. The invention solves the problem of the small movement of regulation and the rapid reaction in the annular gear pumps and variable regulation by means of the support or support of the external rotor of the ring gear operating game that is produced in the outer diameter of the latter in an adjusting ring which preferably has the same width as and which rotates with zero sliding by its pitch circle or outer circumferential circle on an inner pitch circle or inner circumferential circle and the difference in the diameters of the two pitch circles is equal twice the eccentricity of the ring gear set. By maintaining the laws of the internal gear of negative ratio of rotation angle of the eccentric shaft or of the planetary carrier with respect to the rotation angle of the pinion or planetary gear that equals the number of teeth of the pinion when the difference of the number of teeth between the ring and the pinion is the unit. Since according to claim 1 the pitch circle of the external toothing on the adjusting ring is relatively large, for example the number of teeth is 16, the negative angular adjustment of the eccentric shaft is 16 times the angle of rotation of the ring. fit around its own axis. According to this, the adjusting ring executes small angular rotations and in this way small adjustment movements since it merely executes a small rolling movement in the cover. In this arrangement, it is merely necessary that the difference in diameter of the circles rolling internally one over the other is equal to twice the eccentricity of the gear set such that the axial spacing of the gears remains precisely constant during the complete actuation. of regulation. In addition, the circles roll one over the other with zero slip.

To ensure the bearing with zero slip, an aspect according to the invention is proposed in which the pitch circles of the adjusting ring and the cover are formed by the pitch circles of an adjustment gear configured as a complete internal gear or partial that has the same eccentricity as the eccentricity of the ring gear set. Due to the small adjustment movement of the adjusting ring, there is now also the possibility of achieving a reversible pump with a reasonable construction expense in which means are provided to allow the mechanical actuation of the regulating roller adjustment ring movement in both directions from the neutral position (zero position) of the annular gear pump to the supply position, this being a prerequisite for the construction of actuators and hydrostatic controls that also always require an inversion in the direction of rotation. Preferably the toothing of an adjustment gear configured as an internal gear is a trochoid or cycloid internal gear between the adjusting ring and the cover. In the angular range of the cam in which the pump intake is greatly reduced, that is in the region where the toothing of the annular gear of the pump passes the membranes or partitions between the openings or lumens in the form of kidney cover that forms the openings and ports of low and high pressure, there is a risk of cavitation on the suction side and risk of trap formation on the pressure side. To soften the undesirable side effects involved, the adjustment ring comprises, as seen axially, on the opposite side of the openings and ports in the form of high and low pressure kidney, a peripheral connection slot that is closed by the wall of the cover or casing which together with the connecting slots machined in the wall of the cover connects the expansion and contraction displacement cells with one another in the region of the membranes or partitions. A passage connection is provided between these working chambers and allows compensation of the oil flow such that excessive pressure peaks at the location of the trap effect formation and extreme pressure decreases at the cavitation location are avoided. It is especially in the case of pumps required to supply fluids having a very low viscosity such as hot engine oils, where a good sealing of all work spaces, regulation and pressure equalization is important. If, for example, as described in claim 5, the space between the inner circumference of the cover or shell and the outer circumference of the adjusting ring ring serves as a regulating piston, then it is advantageous to provide the precautions, where between the adjusting ring and the cover at least one radially sealed sealing pressure field which is connected to the high pressure is arranged, wherein this pressure field seals the adjustment ring on the opposite side, as radially by its tooth tips or similar tooth-tip portions, against the tooth tips or similar parts of tooth tips of the cover, and / or, where at least one sealing member is provided on the cover, comprising the sealing member on its back between the cover and the sealing member at least one sealed pressure field which sealingly requests at least one sealing member against the tip or tip s of teeth or similar tooth-end portions of the adjusting ring, preferably when exposed to high pressure. The configuration of a zero stroke pump, where the working space for raising the pressure is effective as an adjustment cylinder on the external rotor in the adjusting ring and a regulating spring is provided pushed to move the adjusting ring in the direction of maximum displacement, reduces the cost of the configuration in only compression space in the annular gear pump that way the high pressure itself. Since, however, in the regulation of the supply of the center of moments, that is to say the point around which the adjusting ring rotates in any rotational position, it changes in such a way that in the neutral position of the adjusting ring the component of Hydrostatic force of the work space to be sealed does not already exert a moment on the adjusting ring, the pump is not fully regulated to zero when a spring is used. In this case the working space also exposed to high pressure carries the axially-shaped cross-sectional surface, which can under certain circumstances result in a prohibitively high axial deflection of the cover and more particularly of the housing. This is why the sealing means referred to above are preferably provided. These characteristics of the annular gear pump according to the invention can under certain circumstances prove to be even more advantageous by using known means since it is usual to save costs in the construction of engines to configure the cover mostly from molten aluminum, the set of gears and the sinter metal adjusting ring and the housing often made of metal sheets. In addition, the cost of machining the cover should be minimized so as to be restricted mainly to turning, drilling and rolling using tools driven by numerical control lathes. The external toothing of the adjusting gear is preferably produced integrally with the adjusting ring, more particularly by means of sintering. The external toothing can also be formed mainly by means of a ring stamped with metal foil on the adjusting ring. The internal toothing can advantageously be formed on the cover by means of a stamped metal sheet ring. In another embodiment of the internal ring of the adjusting gear, this is integrally configured with the cover which in turn is preferably sintered together with the internal toothing. The internal rotor of the pump can be housed on the shaft, axially connecting the passages and preferably being provided between the ring grip of the shaft. In an alternative embodiment the internal rotor is integrally configured with the shaft. If the annular gear pump according to the invention is used as a high pressure pump, then the high pressure demands the need to be satisfied by the design, being particularly advantageous when the teeth of the gear set are configured on one of the two rotors as rollers to avoid heavy wear, this also having proven success in rotary piston machines of high pressure and slow stroke. Insofar as the machine is not excessive in its diameter the rollers are preferably arranged in the internal rotor. In this arrangement, especially hard conditions and compact small dimensions are achieved when the internal rotor is integrally configured with the shaft as the support for the rollers. Due to the large surface areas exposed to the effects of the high pressure they produce considerable deformation forces, particularly in the adjusting ring, during the operation of said annular gear pumps. Since these surface areas need to simultaneously form the sliding support for the highly charged external rotor, the hydrostatic force acting from the inside out is more or less compensated from the outside inwards. This can be achieved by the adjusting ring and thus the toothing of the adjusting gear that extends over the entire width of the gear set of the pump and the toothing of the adjusting gear that forms the pressure tight chambers that can be exposed to working pressure or partially to working pressure, as a result of which the forces are compensated radially in the adjusting ring in such a way that the deformations can be reduced to at least a greater degree. The radial compensation force can then also be used to vary the supply of the annular gear pump with the advantage that when the chambers in the gearing of the adjusting gear can be varied both with respect to their number and with respect to their location rotational through the passages and preferably through a rotary control valve within optional limits, as well as can be arranged for use in the case of the aforementioned reversible high-pressure and slow-moving pump machines. The angle of the rotary control valve is variable by • varying the location of the chambers exposed to high pressure and low pressure. The moment required to vary the position of the adjusting ring is materialized by the force vector resulting from the partial pressure field in the toothed chambers of the setting gear exposed to the pressure, preferably at a high pressure, directed beyond the moment center M as the pivot point in such a way that due to the rotation of the pressure field a lever arm materializes simultaneously. The adjusting ring will then rotate in the toothing of the adjusting gear until there is balance between the adjustment moment and the moment exerted by the working pressure field with respect to the new moment center M in the counter-rotation direction. Especially in the case of an annular gear pump for a closed loop application, it is advantageous to provide, at the end of the pump shaft, opposite the drive mass, a regulating and sweeping pump which by known means and known modes replace the External losses through check valves in the low pressure range with greatly reduced pressure. Restraints are preferably provided in the passages for the rotation control valve and the rotation control valve comprises spill openings to connect the chambers in the leakage spaces to the tank. This type of pressure compensation and variation of the supply of the annular gear pump according to the invention requires precise machining of the gearing of the adjusting gear in such a way that drip losses from the compensation and regulation field within the area of suction or within the loss spaces, ie the so-called losses of the annular gear pump, remain within reasonable limits. This is the most important in the case of a variable supply pump since the percentage of losses involved in the effective increase in supply in any case when the pump is discharged (Note: regulated to zero or near zero supply) a uniform pressure in such a way that the volumetric efficiency falls correspondingly strongly. When, on the other hand, the variation of the supply of the adjustment ring is not made directly in hydraulic form, as described above, but is carried out mechanically, as set forth in claim 6, the cells or chambers between the teeth of the adjusting gear exposed to the high pressure merely serve to compensate the forces and thus the stresses in the adjusting ring to minimize the deformation thereof. In this case the number and selection of the cells exposed to the high pressure can be selected in such a way that the adjusting ring always keeps the tips of the teeth of the adjustment gear in contact with each other due to the internal working pressure. In this case both parts, ie the adjusting ring with its internal toothing and the cover ring with its internal teeth, can be produced with sufficient precision by sintering. Then, a sufficient set of teeth can be provided to compensate tolerances. In the case of a high pressure pump an extremely compact design is an important requirement. Spaces exposed to pressure must not comprise any effective large surface area subject to high pressure. This is because in the case of a zero stroke pump the appearance of the same is preferred, wherein the spring force causes the adjusting ring to rotate in the direction of maximum supply; preferably the spring force is transmitted by means of a pressure member to a tooth flank of the external teeth of the adjusting ring. Here, too, there is the problem that the supply can not be brought to zero completely if only the pressure space of the internal annular gear pump is used as an adjustment force in the direction of the zero stroke, since in this position there is no additional adjustment time with respect to the pole of the moment of the adjustment ring. The means available to remedy this situation involve the adjusting ring which, with the increasing rotation, exposes suitable passages or at least one of such passages which guides or guides the high pressure in such chambers or cells in the auxiliary teeth between the adjusting ring and the part of the cover to promote the rotation of the adjustment ring in the direction of the zero stroke. When the toothing between the adjusting ring and the cover part is produced by sintering, there is a requirement, as mentioned above, that an optimum seal be produced by the tip of the teeth in contact with the teeth. This is affected not only by the pressure of. work under compensation but also by the radial components of the tooth force at the moment center M. This is because it is advantageous to select for the toothing of the adjusting gear a tooth shape having a large coupling angle at the full point mesh. This requirement is achieved by means of a trochoid toothing having circular or hypocycloidal teeth on the ring. The axial termination of the adjusting ring in the cover is advantageously configured so as to be substantially smaller than the axial termination of the gear set. Preferred embodiments of the invention, by way of example, will now be explained with reference to the drawings in which: The figure shows a first exemplary embodiment of a reversible pump in a first extreme maximum supply position; Fig. Lb is the reversible pump shown in Fig. 1 in its zero position; The figure is the reversible pump shown in the figures la and lb in a second extreme position of maximum supply; Figure 2 is a longitudinal section through the pump as shown in the figures the a; Figure 3a shows a first exemplary embodiment of a zero stroke pump in its extreme position of maximum supply. 3b is the zero stroke pump of figure 3a in its zero position; Figure 4a shows a second exemplary embodiment of a zero stroke pump in its extreme position for maximum supply. Figure 4b is the zero stroke pump shown in Figure 4a in its zero position; Figure 5 is a longitudinal section through the pump shown in Figure 4a; Figure 6a shows a further exemplary embodiment of a regulated pump, more particularly, for high pressure applications; Figure 6b is a longitudinal section through the pump shown in Figure 6a; Figure 7a is a cross section taken through the pump shown in Figures 6a and 6b; Figure 7b is a partial sectional view of the pump shown in Figures 6a to 7a; Figure 8a shows the regulated pump shown in Figure 6a in a first extreme maximum supply position with positive supply direction; Figure 8b is the pump shown in Figure 8a in its zero position; Figure 8c is the pump shown in Figures 8a and 8b in its second extreme maximum supply position with negative supply direction; Figure 9a shows a further exemplary embodiment of a zero stroke pump; Figure 9b is the pump shown in Figure 9a in its zero position and Figure 9c is a longitudinal section through the pump shown in Figures 9a and 9b; Figure 10 shows a variant of the exemplary embodiment shown in Figure 9a; Figure 11 is a cross section A-A as shown in Figure 10; Figure 12 is a cross section B-B as shown in Figure 10; and Figure 13 is an X view as shown in Figure 11.

An annular gear pump illustrated in the drawings, the a 2 comprises an internal rotor 3 and an external rotor 4 which form, by means of their external and internal teeth, a set of annular gears 5. The external toothing of the internal rotor 3 has a less than the internal toothing of the external rotor 4. The internal rotor 3 is mounted by means of strapping on a driven rotating shaft 2. Axial connecting passages 48 are provided between the shaft with the strapping assembly and the internal rotor 3. Both the axis 2, and thus the internal rotor 3, and the external rotor 4 are rotatably supported on a pump cover, the parts of which are identified by 1, 1 'and 1". The axis of rotation of the external rotor 4 runs parallel and separated from, ie eccentrically of, the axis of rotation of the internal rotor 3, this eccentricity or spacing being identified between the two axes of rotation by means of the reference number 17. Internal rotor 3 and external rotor 4 form between them a fluid supply space. This fluid supply space is divided into cells or displacement chambers 7 each of which is sealed with respect to the others. Each of the individual displacement cells 7 is formed between two teeth in sequence of the internal rotor 3 and the internal toothing of the external rotor 4 each two teeth, in sequence, of the internal rotor having a tip and flank contact 6 with each two teeth in sequence of the opposing teeth of the internal toothing of the external rotor 4. In the lateral cover to the displacement cells 7 are machined adjacent grooves in the form of kidney 8 and 9 which form a fluid supply and a fluid discharge to and from the displacement cells 7 respectively. In the position of the external rotor as shown in the figure the slot 8 forms the low pressure opening or port for the fluid supply and the slot 9 forms the high pressure opening or port for the discharge of fluid. The slot 8 extends from the vicinity of a complete coupling location in the region of the partition or membrane 11 corresponding to the cover in a semicircular shape proximate to the vicinity of an open coupling location that is covered by an additional membrane or partition 10 corresponding to the diametrically opposed cover to the partition 11. The slot 9 on the high pressure side as shown in the figure extends in the cover in mirror-like symmetrical form with respect to the slot 8 on the opposite side from the two partitions 10 and 11. From the complete coupling location in the partition 11 to the open coupling location in the partition 10 the displacement cells 7 are increasingly configured in the direction of rotation D before subsequently becoming smaller from the Coupling location open to the complete docking location. In the rotary drive of the internal rotor 3 the fluid is sucked by the expanding displacement cells 7 in the region of the low pressure opening or port 8., is transported to the open coupling location and is reloaded with high pressure through the high pressure opening 9. In the position shown in the figure the rotation axis of the external rotor 3 is located in the straight line that extends from the complete coupling location through the axis of rotation of the inner rotor 3 to the open coupling location, i.e. towards the open coupling location displaced with respect to the axis of rotation of the inner rotor 3. In this position of the eccentricity 17 and the direction of rotation D the maximum flow or maximum displacement of the low pressure side 8 towards the high pressure side 9 is achieved.

To vary the flow range "V" the external rotor 4 is received by a ring 14 which in turn can be varied with respect to the cover. Freely supported in a rotatable manner in this adjusting ring 14, an external rotor 4 is arranged through its outer circumference 13 by means of a sliding rotating bearing 12. The adjusting ring 14 comprises an external toothing 24 which engages with an internal toothing 24 '. The internal toothing 24 'is connected non-rotatably to the cover. Its central point coincides with the axis of rotation of the internal rotor 3. In the exemplary embodiment of the internal toothing 24 ', this is configured on a stamped ring 27 of metal plate that is rigidly secured to the cover part 1'. or to the part of deck 1 (figure 2). The internal toothing 24 'could, however, also be configured directly integrally with the cover. The cover together with the internal toothing 24 'and the adjusting ring 14 with the external toothing 24 form an adjusting gear 20 for varying the angular position of the external rotor 4 with respect to the internal rotor 3. For this purpose the internal toothing 24' it comprises at least one more tooth than the external toothing 24 of the adjusting ring 14. In the exemplary embodiment, the difference in the number of teeth is precisely one. Furthermore, the difference in the diameter of the inner circle of the internal toothing 24 'with respect to the outer circle of the external toothing 24 is twice the eccentricity 17. When the adjusting ring 14 is now rotated in the direction of rotation D of the internal rotor 3 around the angle? relatively small. a continuous mutual coupling of the two toothes 24 and 24 'of the adjusting gear 20, such that the outer circle 15 of the adjusting ring 14 and the inner circle 16 of the internal toothing 24' roll over each other with sliding zero, the axis of rotation the external rotor 4 deviates from the position shown in the figure the opposite to the direction of rotation of the internal rotor 3 by 90 ° about the axis of rotation of the internal rotor 3 firstly towards the position that is shows in figure lb. The position as shown in figure lb is the zero position of the pump where the ideal case is given in which no fluid is supplied. In the zero position the slot openings 8 and 9 extend symmetrically on both sides of the complete and open coupling locations. In the figure the pump as shown in the figures la and lb is illustrated in its second extreme position. In this position the fluid is supplied from the slot opening 9 now effective as the low pressure opening towards the slot opening 9 which is correspondingly effective as the high pressure opening. For this purpose, the adjusting ring 14 uu further rotated along an additional angle? in the direction of clockwise rotation. The pump of the exemplary embodiment, as shown in the figures, is regulated by means of mechanical drive means. For this purpose uu has two pivoting levers 41 and 43, two brazuti, which pivot about a shaft 42 parallel or spaced the axis of rotation of the internal rotor 3 between end positions, ie those shown a the figures and him The pendulum movement of the rotary lever 41 or 43 is obtained by motive means (not shown). The rotating lever 41, 43 is mounted on the cover part 1 and is enlarged between the two side cover sections 1 'and 1". The rotational axis 42 of the lever 41, 43 is located, as seen in the zero position shown in Figure lb, in the same plane as the axis of rotation of the external rotor 3 and the axis of rotation of the rotor internal 4. The front lever arm 41 which points from the axis of rotation 42 of the lever towards the two above-mentioned axes of rotation is coupled to the adjusting ring 14 at its front end, allowing rotation about a parallel axis 44, lever arm 42. The axis 44 being also located on the zero position as shown in FIG. From this zero position the front arm 41 of the lever is pendulous to both ladoti. The angle ? Above mentioned is the angle along which the adjusting ring 14 rotates about its own axis in the actuation of the lever arm 41. In Fig. 2 the pump is illustrated according to section A-A of Fig. lb. The rotatably driven shaft 2 is rotatable and slidably mounted in the two cover portions 1 'and 1"arranged juxtaposed, as seen in the longitudinal direction of the shaft 2, including between them the rotation parts of the gear pump annular and sealed with respect to the outside by means of a seal. The fluid supply and discharge are provided in the cover part 1", the two slot openings 8 and 9 in the cover portions 1 'and 1". The adjusting ring 14 is provided only at one axial end with the external toothing 24. The ring 27 of the metal plate in turn is applied to a circular cylinder 1 surrounding the adjusting ring 14 and forms an intermediate cover between the two cover casings 1 'and 1' '. The inner circumferential surface of the intermediate cover 1 and the external circumferential surface of the adjusting ring 14 form, in their non-toothed potions, cylindrical rolling surface areas 26 and 29 on which the adjusting ring 14 rolls with a zero slip with respect to the cylindrical intermediate cover 1 due to the adjusting gear 20. The pitch circles 15 and 16 of the adjustment gears are located in the cylindrical rolling surface areas 26 and 29. As seen in the axial direction, the adjusting ring 14 it comprises on the side opposite the high-pressure and low-pressure openings in the form of kidney 8 and 9 a connecting slot 45 in a full circle or half circle closed by the wall 1 'of the cover which together with the connecting slots 46 and 47 (FIG. 5) machined in the wall of the cover connect the expansion and contraction displacement cells 7 with one another in the region of the t abyss 10 and 11. Figures 3a and 3b show a zero stroke pump that is variable between a vacuum position, the zero position, and an extreme position for the maximum flow range. In addition, means are provided to limit the flow range V with an increase in speed in the inner rotor 3. For this purpose, the component part formed by the adjusting ring 14 and the external rotor 4 is adjusted against the force exerted by a spring. regulation 36 which is configured as a compression spring, that is, using the high pressure working space 35 of the pump as a cylindrical space through the external rotor 3 as the regulating piston.

The regulating spring 36 is preloaded by pressure between a first non-rotating articulation assembly on the outermost circumference of the adjusting ring 14 and a second articulation assembly configured as a rotary mounting on the cover such that the regulating spring always it is requested to push the adjusting ring 14 to its extreme position for maximum supply. To allow the external rotor 4 or the adjusting ring 14 to be used as a regulating piston, the high-pressure working space of the pump to be used simultaneously as the working space of the cylinder 35 must be located above the inner circumferential surface area of the external rotor 4 such that the adjusting ring 14 is rotated against the force of the adjusting spring 36 in the adjusting gear 20, as a result of which the pump is automatically adjusted to the zero position with increasing speed and in this way the pressure on the pressure side increases. Making use of the working space of the pump 35 as the cylinder space to vary the movement of the adjusting gear 20 results in a simpler construction of the pump. The high-pressure working space 35 is furthermore connected to at least one space 86 between the adjusting ring 14 and the inner wall of the intermediate cover 1 to which the internal toothing of the adjusting gear 20 is also configured. The pressure field 86 formed in this way on the high-pressure space 35 forces the adjusting ring 14 against the teeth 87 of the internal toothing 24 'of the adjusting gear 20, these teeth being located radially opposite each other. and the working space 35, Lpu pressure spaces are located such that in the position shown in Figure 3b there is a sufficient loading moment for the spring 36 with respect to the moment center M of the adjusting gear 20 Another possibility of regulating the annular gear pump with increasing speed is illustrated in figures 4a, 4b and 5. In this exemplary embodiment, the adjustment gear in this case indicated with the reference numeral 21 is also configured as a partial internal gear having an adjusting ring 14 only partially provided with external teeth and a metal plate ring 27 which corresponds only partially and which is provided with internal teeth, the external partial tooth is identified with the number 2 and the internal partial tooth is identified with the number 23. The two partial teeth 22 and 23 serve to obtain a zero sliding bearing of the circular surface areas. of bearing 26 and 29 of the adjusting ring 14 and of the cover in the adjustment range. Arranged on the cover is a sealing element 89 which extends over the width of the adjusting ring 14. This sealing element '89 has a cylindrical cross section, the circular embodiment being in the exemplary embodiment. The sealing element 89 pressurizes against an elevated face of the tooth location 88, punctual type, which opposes in its configuration the adjusting ring 14 as the counter-sealing location. The sealing element 89 and the raised face 88 are disposed roughly diametrically opposite to the partial dentitions 22 and 23 such that between the sealing location 88 and 89 formed therebetween and the partial dentition 22 and 23, it is this pressure exerts on the outer circumferential surface of the adjusting ring 14 within a space 28, this pressure being exerted on the external circumference of the adjusting ring 14 and thus the adjustment ring is used as a piston. adjustment against the force of a regulating spring 3_i comparable to the regulating spring 36 of the previous example. The sealing element 89, as seen in the regulating spring 32, it is mounted on the rear side of the raised face 88 and configured in the form of a lip for positioning the regulating spring 32 on the adjusting ring and pressing against this raised face 80 which is on the cover. Acting on the back 85 of the sealing element 89 is a fluid pressure field generated between the rear part 85 of the sealing element 89 and the cover and which firmly and sealingly requests the sealing element 89 against the regulating spring 88 yet when it is moved under the sealing element 85 in the course of variation movement of the adjusting ring. The pressure space 28 used as the adjusting cylinder is exposed to the high pressure of the pump on the outer circumference of the adjusting ring 14, this space 28 being located on the outer circumference of the adjusting ring 14 roughly above the opening of high-pressure slot 9 and is connected to slot opening 9 by radial passages 9a which are machined in the cover. As best seen in the longitudinal section of Figure 5, the sealing element 89 is formed by a sealing bushing which is mounted to rotate about an axis parallel to the axis of rotation of the inner rotor 3. It is also quite evident from the 5 shows the connection of the cells and displacement chambers of expansion and contraction of the pump by means of the circumferential connection groove 45 and the two radial grooves 46 and 47 as already described in relation to the illustrated embodiment in figure 1. Illustrated in the subsequent figures 6a to 9c, there can be seen variable supply pumps which are particularly suitable for the application as high pressure pumps. The teeth of the inner rotor 51 are formed by rollers 50, these rollers being cylindrical and circular in the exemplary embodiment, and being mounted to rotate around axes that are parallel to the axis of rotation of the internal rotor 51. The internal rotor 51 eut. It is integrally constructed with its drive shaft, as seen particularly in FIG. 6b. In order to further reduce the deformation forces of the adjusting ring 14, the toothing 52 and 53 of the adjusting gear 20 extends over the totdl width of the adjusting ring 14, as a result of which the ring-shaped cover part 55 forms at the same time. time, together with the internal toothing 53, the intermediate cover between the two cover parts 1 'and 1". To further reduce the load, especially in the adjusting ring 14, the adjusting ring 14 is exposed to the pressure of the high pressure side in the region of its external circumferential surface area extending over the high pressure side of the pump, as seen in radial form. The outer circumferential surface area of the adjusting ring 14 extends over the low pressure side of the pump and is exposed to low pressure. For this purpose, the adjusting gear 20 forms by means of its toothing 52 and 53 pressure-tight chambers 56 'on the high pressure side and pressure-tight chambers 56"on the low pressure side. The pressure-tight chambers 56 'and 56"are connected through passages 58 in a cover portion 57 (FIG. 6b) to the suction and pressure spaces, ie to the high-pressure and low-pressure side of the pump. . The passages 58 open into the inner portions of the internal toothing 53 in the intermediate cover 55. In the cover part 57 at least one connection passage 60 leads to an opening slot 9 and an additional connecting passage 61 located diametrically opposite, opens into the slot opening 8. The connection passages 60 and 61 are connected by means of a rotary control valve 59 to passages 58. As shown in figures 6b, 7a and 7b the rotary valve control 59 comprises a rotating element cylindrical and circular which is rotatably mounted on the cover part 57 concentrically to the axis 2 and is angularly positionable in this arrangement. By connecting the passages 60 and 51 or 61 and 58 the slot openings 8 and 9 are each correspondingly connected to their rear pressure chambers 56 'and 56' 'formed by the toothing 52 and 53 of the adjusting gear. The chambers 56 'and 56"are thus exposed to the pressure of the slot opening or slot assigned thereto. The connection between passages 60 and 58 or 61 and 58 occurs through restrictors 74 and 75 in passages 60 and 61 and the end sections of passages 62 and 63, these end sections of passages 62 and 63 being, in the example of embodiment, formed by simple perforations that are connected through connecting passages in the rotary element of the rotary control valve 59 to the passages 58 that open into the vicinity of the inner circumference of the internal toothing 53. By rotating the rotary control valve 59 the position of the chambers 56 'and 56"exposed to the high pressure and to the low pressure is changed, that is to say the chambers 56' and 56 '' are pressurized selectively corresponding to the angular position of the rotary control valve. In the exemplary embodiment, as evidenced by Figure 7a, an additional passage 77 and 79 provides the vicinity of the passages 60 and 61 respectively. Due to the rotary control valve 59 or the rotating member thereof and the connecting slots provided therein, the passages 60 and 61 are optionally connected to the passages 58 assigned thereto or by means of spill openings 76 and 78. in the rotation element of the second pair of passages 77 and 79 is connected with the loss spaces 80 to the tank 81, as a result of which the pressure chambers 56 'and 56"are optionally pressurized or connected to the loss spaces . Because the pressure on the teeth 52 and 53 of the adjusting gear is variable and because the resultant force is likewise capable of being varied by means of the rotary control valve 59 under the control of at least its direction so that the force vector indicates to one side of the moment center M representing the joint of the adjusting ring 14, the force vector of the partial pressure of the chambers 56 'and 56' 'acting on the adjusting ring 14 a through the lever arm formed as a moment of variation. The adjusting ring 14 rotates due to the effect of this moment in its equilibrium position in which the moment of variation acts without the moment of the working pressure between the internal rotor and the external rotor 51 and 54 which are in equilibrium with respect to to the respective moment center M, thus resulting in a range of flow that is achieved oriented according to the requirement.

As illustrated in FIG. 6b, a variable displacement and sweeping pump 72 is disposed at the end of the axis 2 opposite the drive core, this pump replacing the external loss fluid in the case of a closed circuit through valves retention 73 in a range of low pressure with a greatly reduced pressure. In addition, the rotary control valve and the cover portion 57, as indicated in FIG. 7a, comprise the spill openings 76 and 77 as well as 78 and 79 connecting the chambers 56 'and 56"with the spaces of loss 80 towards the fluid container. This control arrangement, as is known, is switchable in the case of orbital-piston motors. When for example 16 chambers 56 'are provided, there are 30 switching openings in the regulating ring 59 which alternately connect the suction and pressure slot openings. Since such contiol provisions are well known in general, it is not necessary to give explanations in this regard. The control of the inclination of the rotary control valve 59 is made by means of the adjustment mechanism shown in FIGS. 7a and 7b, wherein a rotating lever 64 acts in a manner similar to the manner in which the rotary lever 41 and 43 were used to vary the movement of the adjusting ring 14 in the exemplary embodiment shown in Figures a to 2. The lever 64 is mounted on the cover to restrictively oscillate around an axis oriented parallel to the axis of rotation of the internal rotor 3. By means of a free end the lever is coupled through a ball joint to the rotary element of the rotary control valve 59. This simple and simple lever G < 1 pivots by means of its projecting end beyond its axis of rotation with respect to the opposite side by means of dou linear variable displacement means 65 which oscillate the lever 64 about its axis of rotation forward and backward, as a result of which the position of the rotating element of the rotary control valve 59 varies within a restricted angular range. Figures 8a to 8c illustrate the end positions and the zero position of the gear pump;] in rings according to figures 6a to 7b. The pump as shown in Figures 8a to 8c is configured. as a reversible high pressure pump. In figures 9a to 9c there is illustrated a high pressure pump that has automatic regulation. In the exemplary embodiment of FIGS. 9 a to 9 c, a zero stroke pump having a spring loaded member 93 on one side 94 of the cover is merely illustrated. A second reverse specular arrangement of a second spring loaded member 93 'is merely suggested on the side 95 of the cover, opposite that of member 93. Due to the possible disposition of a second spring loaded member 93', the pump, as shown in Figures 9a to 9c, it is also configured as a zero stroke pump for both directions of rotation. The adjustment ring 14 eat? requested through a member 93, on which a regulating spring 117 acts, against a flank of the external toothing 24 of the adjusting ring 14 in a position of maximum supply in one direction. The spring 117 acts in the same manner as the springs 32 or 36 that were described above. The second member 93 ', which can be in the same way jointly requested with its regulating spring from the other side with respect to a tooth flank of the external toothing 24, forces the adjusting ring 14 in the direction of maximum supply in the direction opposite. In this arrangement the member 93 or the other member 93 'is already, depending on the direction of rotation, in a flank coupling with the external toothing 24. By means of the members 93 and 93' which are elastically requested against their respective Tooth flanks of the external toothing 24 were configured a zero stroke pump having automatic regulation as the embodiments of Figures 3a to 4a. The zero stroke pump can be prepared by the manufacturer in such a way that it can be incorporated either as a rotary pump in a clockwise or anti-clockwise direction, depending on the circumstances of the final position of the cover 'which is prepared for both directions of rotation, simply incorporating the member together with the spring according to the desired need of the direction of rotation. This pump could still be configured as a reversible pump by means of an adjustment mechanism, for example a positioning cylinder acting on the adjusting spring 117 in order to control the change in the position of the spring 117. As described above with respect to to Figures 6a to 8c the adjusting ring 14 is pressurized in its external circumferential surface area by means of the chambers 91 'and 91"connected to the high pressure side and the low pressure side is formed by the toothing 24 and 24 'of the adjustment gear. For this purpose, the high pressure side and the low pressure side are connected through the chambers 92 'and 92", leading to the inner circle of the external toothing 24', towards the respective chambers 91 'and 91". By at least one slot 96 provided on the high-pressure side, in the case of a reversible pump, on both sides, on the cover and connecting several chambers 91 'or 91"to one another, a particularly suitable adaptation is achieved and of the external pressurization of the adjusting ring 14. The force acting on the adjusting ring 14 due to the pressure in the working spaces of the pump 90 'and 90"is less than the force exerted on the adjusting ring 14 due to the pressure in the outer pressure spaces 91 'and 91", although it is applied in the same way to the other pumps that have automatic regulation by means of said pressure fields. This is achieved by the radially pressurized effective surface area in the working spaces 90 'and 90", which are still smaller than the radially effective surface area of lou pressure spaces 91' and 91". The position of the adjusting ring 14 is thus dictated by the force vector resulting from the pressure in the working spaces 90 'and 90' 'and the pressure spaces 91' and 91 ''. In figure 10 there is illustrated a variant of the zero stroke or reversible pump having automatic regulation as shown in figures 9a to 9c, so that the teeth of the internal rotor are again configured integrally with the internal rotor. To facilitate the manufacture of the toothing between the adjusting ring 14 and the cover part 102, the external teeth 100 are circular or partially circular in shape, according to a cross-section of the adjusting ring 14, which facilitates, more particularly, the manufacture of the coupling toothing 103 on the cover 102. The coupling toothing 103 is formed by means of a sheet lamination of high speed, the radius of which is equal to the radius 104 of the external toothing 100. The axis of rotation of the laminate of sheet, that is to say its longitudinal centerline, is guided on a hypocycloid having the same eccentricity 17 as that of the adjusting ring 14. The cover part 102 in this way can be initially manufactured as an integral casting without the intermediate cover, the toothing 103 then being machined by a rolling process, as described. In this way, the cover part 102 comprising the internal toothing of the adjusting gear can be produced particularly economically. In the exemplary embodiment as shown in FIGS. 10 to 13, the cover is composed of two parts, that is to say with the cover parts 102 comprising the internal toothing and a housing part 111. As in the case of exemplary embodiments already described it is basically possible to produce the cover part 102 also in two parts, ie with an intermediate cover part comparable to the cover portions 55 that have been described above.

In the exemplary embodiment as shown in FIGS. 10 to 13, the adjusting ring 14 again comprises on at least one of its axial sides a circumferential groove 45 which produces, through two additional axial grooves 46 and 47 which are preferably configured in the form of housing cover 111 in the region of the partitions between the suction portion 114 and the pressure portion 115, a connection passage between the trap space 112 and the cavitation space 113. The pump in itself it is regulated automatically by means of a regulating spring 117. As explained above in the embodiment example shown in figures 9a to 9c the regulating spring 117 acts through a member 93 on the external toothing 100 of the adjusting ring 14. When a reversible pump having automatic regulation is configured, again here, a second regulating spring 117 can be provided. The resort The regulating member 117 may preferably be additionally configured to form a regulation spring arrangement that includes at least two spring connected in series. In this way the pump according to the invention can be formed with a supply characteristic wherein the pump: performs a rapid increase in flow velocity within a first pump speed range, with a high flow rate proportional to the pump speed in a first approximation, - the pump being within a second higher speed range, quickly adjusted to the zero position until a preset pump speed is reached and - the speed of the pump is again increased rapidly the pump in a third speed range greater than the speed of the second speed range and so on subsequently.

A characteristic of the supply of this type is particularly advantageous for applications in motor vehicles in which a pump according to the invention is driven by means of the motor of the vehicle, thus having the pressure side a fixed relation with respect to the speed of the motor . The motor vehicles require in the lower speed range of the engine, that is to say the start, greater quantities of lubricants supplied directly. After having achieved a predetermined speed of the motor and in this way that the speed of the pump and the supply involved, an appreciable increase in the speed of the flow of the pump through the speed range subsequent to the pre-set speed of the motor is needed. Where the flow range leading to an additional increase without restriction or increase in pump speed, the supply should be in excess of the actual requirement, with a correspondingly high demand for energy for the pump. After passing through the average speed, which is generally at the main operating speed of the engine, a higher lubricant flow is necessary at higher engine speeds because these involve greater centrifugal forces at the locations to be lubricated, for example on the crankshaft. To superimpose on these centrifugal forces a significant gain is required at the higher lubricant pressures. In general, the three speed ranges to be distinguished in the case of passenger motor vehicles are the speed range of the lower motor that ranges from 0 to approximately 1500 revolutions per minute, continuing through the main operating range from approximately 1500. revolutions per minute at approximately 4000 revolutions per minute and the third highest engine speed range that is at approximately 4000 revolutions per minute. To achieve the desired supply characteristic, ie with a stepped increase in the flow rate at the lower speed, continuing with a relatively slow increase or even with a zero increase in the average speed and concluding again with a stepped increase in speed highest, a first regulating soft spring is connected in series to a second regulating spring which is harder compared to the previous one, and both springs form a regulating spring arrangement 117. The regulating spring arrangement 117 as shown in figures 9a, 9c or figure 10, basically also the regulating spring 36 shown in figures 3a to 4b, are used to achieve this delivery characteristic by means of the two regulation springs mentioned. The regulation spring arrangement 117 is installed under preload so that no decrease in the lower speed range occurs. As soon as the pre-loading force is exceeded in the transition from the lower speed range to the medium speed range the first soft space begins its spring action until the upper end of the medium speed range comes up to act against the second harder regulating spring, until stopping. With a further increase in speed the supply characteristic is then commanded by the second hardest regulating spring. When the present pump is put into use as a lubrication pump for internal combustion engines, more particularly for motor vehicles, the pump according to the invention can be used not only as a lubrication pump, it can also be advantageously used for pumping the pump. lubricant to a hydraulic valve play compensation device and / or as a pump to regulate the timing of the valves. For these applications, it can be used for each application alone or in combination with other pumps. However, the pump according to the present invention is suitable for these purposes basically in all the described variants, since it has been adapted with a high fairness basically to any desired delivery characteristic because it is infinitely variable .

Claims (24)

CLAIMS Having thus specially described and determined the nature of the present invention and the manner in which it is to be brought into practice, it is claimed to claim as property and exclusive right:

1. An annular gear pump with infinite regulation, comprising a) a stationary cover; b) an internal rotor in the cover, rotatably supported and driven by means of an axis, and c) an rnal rotor in the same way supported in a rotating manner, coupled with said internal rotor; d) the difference in the number of teeth of the annular gear set comprised by said internal rotor and said rnal rotor equal to the unit, having a tooth shape in which a plurality of expansion and contraction displacement cells, each sealed with respect to the other, they are formed due to the punctual contact between teeth, and e) low pressure and high pressure openings are provided on the cover in the form of a kidney, arranged stably and laterally in the region of said displacement cells, said openings being separated from one another by means of partitions and f) the angular position of the eccentric axis (eccentricity) of said set of annular gears is variable to the cover, where: g) the support of said rnal rotor of said ring gear set it is produced in the outer diameter of the latter in an adjusting ring, which preferably has the same width, and which is rolling with slip. or zero by its outer circle or pitch circle, on an inner circle or pitch circle and h) the difference in the diameters of said two pitch circles is equal to twice the eccentricity of said set of ring gears.

2. The pump according to claim 1, wherein said passage circles of said adjusting ring and said cover, which roll with zero sliding one on the other, are formed by passing circles of an adjusting gear configured as a complete internal gear. or partial that has the same eccentricity as said eccentricity of said ring gear set.

3. The pump according to claim 1 or 2, wherein said internal gear is formed by an rnal toothing on said adjusting ring and an internal toothing on said side of the cover, said internal toothing having to be coupled with the flanks of said rnal toothing. at least one tooth, preferably only one, more than said rnal toothing, this difference being in the case of only the partial teeth, related to the completely circumferential imaginary teeth.

4. The pump according to any one of the preceding claims, wherein the teeth of an rnal toothing for forming an adjustment gear have a rolling action with zero sliding and are only arranged laterally on said adjusting ring, and the remaining width of said adjusting ring serves as a cylindrical rolling surface area.

5. The pump according to any of the preceding claims, wherein to form a zero stroke pump a space is provided between a wall of said cover forming said inner circumferential circle and a wall of said adjusting ring forming said outer circumferential circle, the pressurized space being on the pressure side and said adjusting ring is used as an adjusting piston which acts against a regulating spring to produce the regulating rolling movement of said adjusting ring.

6. The pump according to any one of claims 1 to 4, wherein to form a reversible pump means are provided which allow the mechanical actuation of said regulating bearing movement of said adjusting ring in both directions from the neutral position (position zero) of said annular gear pump to the supply position.

7. The pump according to any of the preceding claims, wherein between said adjusting ring and said cover there is disposed at least one pressure field which acts radially and is sealed, and which is connected to said high pressure, wherein said field of pressure seals said adjustment ring on the opposite side as viewed radially by its tooth ends or similar tooth-tip portions thereof, against the tooth tips or tooth-like portions of said cover.

8. The pump according to any of the preceding claims, wherein on said at least one cover a sealing member is provided, said sealing member comprising on its rear part between said cover and said sealing member at least one sealed pressure field which sealed it requests said at least one sealing member against said tooth tip or tips or similar tooth-tipped portions of said adjusting ring, preferably exposed to the high pressure.

9. The pump according to any of the preceding claims, wherein to form a zero stroke pump the pressure generating work space is effective as an adjustment cylinder on said external rotor in said adjusting ring and a regulating spring is provided. pushed to move said adjusting ring in the direction of maximum displacement.

10. The pump according to any of the preceding claims, more particularly for use with high pressure, wherein said teeth of said set of annular gears forming said displacement cells are configured on one of said two rotors as rollers, said rollers being mounted rotatingly in said respective rotor.

11. The pump according to any of claims 2 to 10, wherein the toothing of said adjusting gear extends over the entire width of said set of annular gears.

12. The pump according to any of claims 2 to 11, wherein said adjusting gear forms pressure-tight chambers that are in a part of the cover in connection with the pressure and suction spaces respectively of said pump, through passages

13. The pump according to any of the preceding claims, wherein through a rotary control valve said chambers can be expueted both in relation to the number and the location, each one opposite the high pressure and the low pressure through passages. .

14. The pump according to claim 12 or 13, wherein the sum of the surface areas exposed to the high pressure in said pressure chambers between said adjusting ring and said cover has an effect of force less than the sum of the exposed surface areas to the pressure in the working chambers in said pump toothing.

15. The pump according to any of claims 1 to 14, wherein to form a zero stroke pump a spring exerts a force to rotate said adjusting ring in the direction of maximum supply; preferably said spring force is transmitted by means of a pressing member towards a tooth flank of said external toothing of said adjusting ring.

16. The pump according to any of the preceding claims, wherein several tooth chambers located on the pressure side between said internal toothing of said cover part forming said adjusting gear and said external toothing of said adjusting ring, are connected to through passages with the high pressure and said tooth chambers located correspondingly in the opposite way are connected with the low pressure through passages.

17. The pump according to claim 15 or 16, wherein said passages are arranged in such a way that they are closed with respect to the high pressure and / or connected to the high pressure, one after the other, in a reduction in the displacement of the rotary movement of said adjusting ring.

18. The pump according to any of claims 15 to 17, wherein pressure members are arranged on both sides of said cover, said pressure means being operable by an adjustment cylinder to form a reversible pump.

19. The pump according to any of claims 15 to 18, wherein in the region of said adjusting gear between said adjusting ring and said cover grooves are machined in the circumferentially oriented laterally disposed cover part, said grooves connecting the tooth chambers of said toothing with one another on the high pressure side or on the low pressure side or on both sides at a suitable length to rotate the hydraulic forces in these areas.

20. The pump according to any of claims 15 to 19, wherein an arrangement of regulation springs for generating the spring force comprises at least two springs, and in a first regulation range a spring-spring characteristic having a small increase in force and in the second second regulation range, another characteristic that has a greater increase in force are provided through a regulatory trajectory.

21. The pump according to any of the preceding claims, wherein said adjusting ring comprises on at least one axial side a circumferential groove that produces through at least two additional axial grooves preferably arranged in a cover part similar to a carcass a connection passage between the trap space and the cavitation space in the partition portions between said suction portion and said pressure portion.

22. The pump according to any of the preceding claims, wherein said adjusting ring comprises an outer circular toothing on its outer diameter to form said adjusting gear and said cover is formed as an internal toothing by the rolling action of said adjusting ring which has said eccentricity in common with that of said ring gear set.

23. The pump according to claim 22, wherein said cover is produced by casting and said tooth shape of said internal toothing is formed by a laminate cut.

24. The pump according to any of the preceding claims, wherein said pump is used to supply a hydraulically operated adjusting means for adjusting and regulating the control of the timing valve of a valve-controlled internal combustion engine. SUMMARY An infinitely adjustable annular J-gear pump comprising a stationary cover, an internal rotor in the casing rotatably supported and driven by means of a shaft and an external rotor equally rotatably supported, which meshes with said internal rotor , the difference in the number of teeth of the annular gear set comprised by said internal rotor and said external rotor equal to the unit, having a tooth shape in which a plurality of expansion and contraction displacement cells, each sealed with respect to the other, they conform due to the punctual contact between teeth, and provided on the cover low pressure and high pressure openings in the form of kidney, fixedly arranged and laterally in the region of said displacement cells, said openings separated from one another by means of partitions and the angular position of the eccentric shaft (eccentricity) of said set of engr Annular anajes is variable to the cover. The support of said outer rotor of said set of ring gears is produced in the outer diameter of the latter in an adjusting ring, which preferably has the same width, and which is rolling with zero sliding by its outer circle or pitch circle. , on an inner circle or step circle. The difference in the diameters of said two pitch circles is equal to twice the eccentricity of said set of annular gears.