Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member

Definitions

• the invention relates to a gear rotor set for a
• the toothed rotor is similar to a toothed ring pump with a toothed design, the function and mode of operation of a toothed rotor set which corresponds to a toothed ring pump.
• the pressure chamber is not separated from the suction chamber by a sickle-shaped filler, but a special design of the teeth - based on the trochoid toothing - ensures the seal between the gerotor ring and the externally toothed pinion.
• the internally toothed toothed ring has one tooth more than the pinion, so that the tooth heads touch exactly opposite the tooth engagement point if the teeth are designed accordingly.
• This head play causes internal leaks in the gerotor pumps and thus a poor volumetric efficiency. As a result, high pressures cannot be built up at low speeds.
• a pump according to the teaching of DE-A-196 46 359 is more advantageous compared to gerotor pumps.
• the pump forms a generic toothed rotor set consisting of a
• FILLING HEAD has the same module in which the teeth of the gear mesh.
• the function of the gear rotor set results from the fact that a drive torque acts on the inner rotor via a drive shaft and rotates it.
• a force is transmitted from the toothed inner rotor to the planet gear, which on the one hand results in an impact force through the center of the planet gear and a circumferential force which brings about a torque of the planet gear.
• the impact force that acts on the bearing ring causes it to rotate.
• the generic toothed rotor set proves to be disadvantageous in that clean rolling without interference is not guaranteed under all operating conditions.
• the movement of the planet gears relative to the bearing ring comes to a standstill in one position.
• a toothed rotor set consisting of a rotatable bearing ring with bearing pockets, in which rotatably mounted planet rotors are arranged, which form an internal toothing, with an inner rotor which is mounted eccentrically to the bearing ring and which has an approximately star-shaped outer contour and which is provided with external teeth , wherein the external toothing has one tooth less than the internal toothing and the toothing of at least one of the two rotor systems has an arcuate portion at least in partial areas of the tooth shape of the toothing.
• the advantage of a toothed rotor set designed in this way is that the curved portion of the tooth shape essentially results in rolling friction and no sliding friction, so that wear on the toothing is minimized.
• the convex tooth head of the toothed inner rotor and the concave tooth base of the toothed planetary rotor result in a contact surface and not a line of contact.
• the Hertzian pressure is greatly reduced by this pair of rollers.
• Tooth shape is arcuate. Such a design of the tooth shape in the region of the tooth head and / or the tooth base enables very large impact forces (radial forces) to be transmitted, the proportion of the circumferential force to be transmitted being able to be small.
• the tooth head and the tooth base are included in the rolling process, i.e. the rolling of the toothed planetary rotors on the toothed inner rotor curve, also included.
• the convexly curved tooth flank of the planetary rotor and the concave curved tooth flank of the inner rotor form a relatively large sealing surface during tooth engagement, which seals the displacement chamber when the displacement chamber passes from the suction region into the pressure region. Even deviations in the perpendicularity of the rotor do not lead to leakage losses in the displacement chamber.
• the area of the tooth head and / or the tooth base has a flattened shape.
• the planetary gear In the main zone of the power transmission, in which the torque acts on the bearing ring through the toothed inner rotor via the toothed planetary rotor, the planetary gear almost comes to a standstill due to the geometry. With the described relative standstill and the simultaneous transmission of a large force, there is a risk that the lubricating film breaks down between the planetary tooth head and the bearing ring. To counteract this, the planetary rotor tooth heads were flattened. The size of the flattening depends on the area of application of the gear rotor. At low speeds and high pressures, a strong flattening is necessary.
• the area of the tooth head and / or the tooth base has a large radius of curvature.
• the flattening of the planetary rotor tooth heads also improves the transmission of force (Hertzian pressure) from the planetary rotor to the bearing ring.
• the arcuate portion is at least partially designed as a cycloid.
• the cycloid has proven to be particularly advantageous in terms of rolling behavior and the transmission of the impact forces. This cycloid toothing ensures smooth, low-friction rolling even with considerable changes in curvature and small radii of curvature, which in turn reduces wear.
• the tooth shape is designed as an involute at least in the region of the tooth flanks.
• Planetary rotor formed by an involute with this embodiment, however, interference can more easily occur than with an embodiment whose tooth flanks are designed as cycloids.
• the toothing has a low-wear surface.
• the low-wear surface can be protected by a chemical special thermochemical and / or physical surface treatment can be achieved.
• the surface can also be galvanized. Further advantageous surface treatment processes are caburizing and nitriding and / or nitrocarburizing, boriding and / or chromating.
• At least one fluid channel is arranged in the region of the bearing pockets.
• the fluid channel can be connected to the pressure side of the pump, so that lubricating oil is continuously supplied between the planetary rotor and the bearing pocket in order to ensure an improved lubricating film build-up.
• This circumferential web serves as a seal within the housing in which the toothed rotor set is accommodated.
• Such moving parts usually have a sealing surface on their end faces, which extends over their entire surface with the exception of the toothing.
• the seal according to the invention by means of the circumferential web has the advantage that the high frictional forces occurring in the known seals are greatly reduced and the set of toothed rotors thus works more easily and therefore more efficiently.
• the circumferential web has a width which represents the optimum between the sealing effect and the frictional force.
• the invention relates to a method for producing a toothed rotor set, which is produced in a shaping process, preferably by means of powder metallurgical processes, plastic injection molding, extrusion molding, die casting, in particular aluminum die casting, and stamping processes.
• a complex toothing as the toothed rotor set according to the invention has can be produced simply and inexpensively by means of these methods.
• a filing and sawing, which is known for the usual gears Is used, can not be used in the invention, since the toothing is too complicated.
• the toothed rotor set is used in a pump, in particular a lubricating oil pump for internal combustion engines.
• the gear rotor set is used as a motor.
• Fig. Lb top view of the gear rotor set with suction side and pressure side
• FIG. 2 shows a variant I of the toothing according to the invention according to the detail "X" in Fig. 1,
• Fig. 4 shows a variant III of the toothing according to the invention
• Fig. 5 shows the parameters used for the gear calculation
• Fig. 1 shows a gear rotor set 1 according to the invention, consisting of a rotatable bearing ring 2 with bearing pockets 3, in which rotatably mounted planet rotors 4 are arranged, which form an internal toothing, with an inner rotor 5 eccentrically mounted to the bearing ring 2 with an approximately star-shaped outer contour, which has an external toothing 6 is provided, the external toothing 6 having one tooth less than the internal toothing.
• the toothed rotor set 1 has a suction area 7, a pressure area 8 and a displacement chamber 9.
• a drive torque M1 acts on the toothed inner rotor 5 via a drive shaft 10.
• a circumferential force F2 acts from the toothed inner rotor 5 on the toothed planetary rotor 4, which is mounted in a bearing ring 2 (housing).
• the peripheral force F2 is divided into two components, the impact force (radial force) F3 and the torque M4, both of which act on the toothed planetary rotor.
• the impact force F3 acts through the center of the toothed planetary rotor 4, which is mounted in a bearing ring 2, and sets the bearing ring 2 in rotation.
• the toothed planetary rotor is set in rotation by the torque M4.
• the toothed rotor set 1 according to the invention can be used as a pump for generating pressure by driving the inner rotor 5 via a drive shaft 10.
• the toothed rotor set 1 according to the invention can also be used as a motor by applying pressure to the pressure area, so that the inner rotor 5 is set in rotation and drives the drive shaft 10.
• Fig. La shows the gear rotor set 1 in a second working position. A maximum pressure is generated in this, since the inner rotor 5 works at most on the planetary rotors 4.
• FIG. 1b shows a top view of the toothed rotor set 1, both a suction side 21 and a pressure side 23 being shown.
• An inlet opening 22 opens into the suction side 21 and can, for example, be formed laterally as a bore in the housing accommodating the gear rotor set.
• An outlet opening 24 likewise opens into the pressure side 23. The diameter of the outlet opening 24 is smaller than that of the inlet opening 22, since the latter has a higher flow rate.
• FIG. 2 shows a variant I of the toothing according to the invention according to the detail “X” in FIG. 1.
• the large impact force F3 (radial force) shown in FIG. 1 and the only small circumferential force F4 have to be transmitted.
• tooth head 11 and tooth base 12 are in the rolling process, i.e. the rolling of the toothed planetary rotor 4 on the toothed inner rotor curve is included.
• the surface portions of the toothing were chosen so that they correspond to the distribution of forces.
• the largest portion, the arcuate portion 14, of the toothing thus exists on the tooth base 12 and tooth tip 11, which transmit the impact force F3 between the toothed inner rotor 5 and the toothed planetary rotor 4.
• Only a small proportion of the toothing surfaces consists of sliding surfaces in the area of the tooth flanks 15, which convert the peripheral force F4 into a rotary movement of the toothed planetary rotor 4.
• the tooth head 11.1 of the toothed inner rotor 5 is calculated so that it lies precisely in the tooth base 12.2 of the toothed planetary rotor 4, and it can be rolled off easily. ensures.
• the tooth head 11.2 of the toothed planetary rotor 4 engages in the tooth base 12.1 of the toothed inner rotor 5.
• the convex tooth head 11.1 of the toothed inner rotor 5 and the concave tooth base 12.2 of the toothed planetary rotor 4 result in a contact surface and not a line of contact. Hertzian pressure is therefore greatly reduced by this roller pairing.
• FIG. 3 shows a second variant of the toothing according to the invention.
• a cycloid 20 was used which favors the build-up of the lubricating film more than a simple transition radius.
• the flattening 13 of the planetary tooth heads 11 also improves the transmission of force (Hertzian pressure) from the planetary rotor 4 to the bearing ring 2.
• the tooth flanks 15 of the toothed inner rotor 5 and the toothed planetary rotors 4 being formed by an involute 18.
• the tooth head of the planetary rotor 4 is designed as a cycloid 19. In this embodiment, however, there is a greater probability that interference will occur.
• the stress on the contact line of the tooth flanks is alternatively calculated as the pressure stress of two parallel rollers, which correspond to the tooth pairing in the following points: length b of the contact line, radius of curvature rl and r2 in the cutting plane normal to the contact line, material pairing and surface quality, (rl and r2 are measured at the point of contact of the unloaded flanks)
• the related load is (k value according to Stribeck).
• r2 must be used negatively for concave flanks.
• the toothing of the planetary rotor 4 is designed as a zero toothing and that of the inner rotor 5 contains a negative profile shift.
• Pitch circle 1 (tl) pitch circle of the planetary rotor 4
• Roll circle 3 (r3) of tooth tip 11.2 (epi-cycloid); Rolling circle 4 (r4) of tooth tip 12.2 (hypo-cycloid)
• Tooth thickness d (t / 2 - 2 * bsp)
• Rolling circle 5 (r5) (t / 2 + 2 * Flsp.) / ⁇
• This design of the toothing means that the curvature ratios between tooth head 11 and tooth base 12 (convex, concave) are very similar, which almost touches the surface and thus reduces the Hertzian pressure. Furthermore, with this optimized design for rolling The additional sliding movement (tangential friction force) is very low.
• the toothing according to the invention can also be used for elliptical wheels, general non-circular wheels and Roots blowers.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Gears, Cams (AREA)
• Supercharger (AREA)
• Valve-Gear Or Valve Arrangements (AREA)
• Gear Transmission (AREA)
• Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Priority Applications (8)

Applications Claiming Priority (2)

Related Child Applications (1)

Publications (1)

Family

ID=7908408

Family Applications (1)

Country Status (11)

Cited By (1)

Families Citing this family (29)

Citations (3)

Family Cites Families (1)

• 1999
  • 1999-05-18 DE DE19922792A patent/DE19922792A1/de not_active Withdrawn
• 2000
  • 2000-05-17 JP JP2000618621A patent/JP3670215B2/ja not_active Expired - Fee Related
  • 2000-05-17 AU AU56743/00A patent/AU5674300A/en not_active Abandoned
  • 2000-05-17 EP EP00941957A patent/EP1180217B1/de not_active Expired - Lifetime
  • 2000-05-17 CA CA002372883A patent/CA2372883C/en not_active Expired - Fee Related
  • 2000-05-17 CN CNB008076871A patent/CN1179129C/zh not_active Expired - Lifetime
  • 2000-05-17 MX MXPA01011453A patent/MXPA01011453A/es active IP Right Grant
  • 2000-05-17 BR BR0010627-5A patent/BR0010627A/pt not_active IP Right Cessation
  • 2000-05-17 DE DE50015136T patent/DE50015136D1/de not_active Expired - Lifetime
  • 2000-05-17 WO PCT/EP2000/004474 patent/WO2000070228A1/de not_active Ceased
  • 2000-05-17 AT AT00941957T patent/ATE393881T1/de not_active IP Right Cessation
• 2001
  • 2001-11-19 US US10/053,927 patent/US6540637B2/en not_active Expired - Lifetime

Patent Citations (3)

Non-Patent Citations (1)

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