EP2119869A2 - Hydromachine - Google Patents

Hydromachine Download PDF

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Publication number
EP2119869A2
EP2119869A2 EP20090006163 EP09006163A EP2119869A2 EP 2119869 A2 EP2119869 A2 EP 2119869A2 EP 20090006163 EP20090006163 EP 20090006163 EP 09006163 A EP09006163 A EP 09006163A EP 2119869 A2 EP2119869 A2 EP 2119869A2
Authority
EP
European Patent Office
Prior art keywords
pressure
housing
hydraulic machine
rotor
support
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.)
Withdrawn
Application number
EP20090006163
Other languages
German (de)
English (en)
Inventor
Brian Kane
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2119869A2 publication Critical patent/EP2119869A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/601—Adjustment

Definitions

  • the invention relates to a hydraulic machine according to the preamble of patent claim 1.
  • the axial adjustability of the output rotor serves to vary the gap width between the teeth of the spur gear, so as to determine with a variable short-circuit gap between the working spaces, the flow rate of the delivery unit.
  • the disadvantage here is that rests unevenly by the application of force to the output pin, the rotor on a plain bearing bush and thus locally high bearing forces occur, resulting in poor efficiency and damage to the delivery unit.
  • the invention has for its object to provide a hydraulic machine, which has a long life and high efficiency.
  • a hydraulic machine has a drive rotor and an output rotor whose axes are employed relative to one another. About a spur toothing these mesh together, with adjacent teeth of the spur gear each a working space is limited, the rotation of the rotors with a low pressure area or connection and a high pressure area or connection is connectable. At least one of the work spaces facing away from the back support surface of a rotor is subjected to a support pressure corresponding to a pressure in the work spaces.
  • This solution has the advantage that the support pressure counteracts the pressure in the working spaces and the rotor can thus be hydrostatically relieved, whereby one-sided support and bearing forces of the rotor are reduced, for example, to a warehouse. This results in a lower bearing friction of the rotor and a lower surface pressure between the rotor and the housing and thus a higher efficiency and a longer service life of the hydraulic machine.
  • the drive rotor may have a drive pin provided in a drive bearing and the output rotor may have a driven pin provided in an output bearing, wherein an end face of the output pin and the back support surfaces of the rotors facing away from the work spaces are subjected to the support pressure.
  • the output pin is acted upon by the support pressure from a low-pressure region and the support surfaces of the rotors in each case with the support pressure from a high-pressure region of the hydraulic machine.
  • the hydraulic machine can advantageously be constructed very simply, wherein the rotors are enclosed by a housing with a housing cover.
  • the drive pin of the drive rotor is mounted in a housing and the output pin of the output rotor in a radially stepped back and dipping into the housing cylinder portion of the housing cover.
  • the support pressure can be particularly easily applied to the support surfaces of the rotors when the housing cover a first and the housing have a second pressure pocket, which act on the opposing support surfaces of the rotors each with support pressure from the high pressure region of the hydraulic machine.
  • the rotor can simply be subjected to support pressure if they run concentrically around the respective rotor axis along the support surfaces of the rotors and are arranged essentially in the region of the higher and highest pressure load generated by the working spaces.
  • the pressure pockets are each bounded by an inner and an outer support web of the housing and of the housing cover, which concentrically extend around the respective rotor axis.
  • the support surfaces of the rotors can be supported on the support webs.
  • the hydraulic machine has a rear support space in order to pressurize the output pin of the Abtriebrotors in the direction of the rotor axis with support pressure.
  • This is frontally bounded on the one hand by a recess in the housing cover and on the other hand by a rear end face of the output pin and can be connected to the low-pressure region of the hydraulic machine.
  • the support space will be connected, for example via a first low-pressure channel in the housing cover and an adjoining second low-pressure channel in the housing with the low-pressure region of the hydraulic machine.
  • the first pressure pocket can be connected via a first high-pressure channel in the housing and the second pressure pocket via a second high-pressure channel in the housing cover and an adjoining third high-pressure channel in the housing with the high-pressure region of the hydraulic machine.
  • the low and high pressure channels can be easily introduced as holes or as grooves in the housing cover and in the housing.
  • a material for the rotors reinforced plastic can be used, which is characterized by low friction values.
  • a hydraulic machine which is designed as a delivery unit.
  • the hydraulic machine according to the invention is not limited to such delivery units, but can for example also be used as a hydraulic motor.
  • FIG. 1 is a longitudinal section through a delivery unit 1, for example, a spur gear pump, shown according to a first embodiment.
  • This has a drive rotor 2 and driven by the drive rotor 2 output rotor 4, wherein the two rotors 2, 4 interacting in each case via a spur gear toothing 6.
  • the rotors 2, 4 are encompassed by a housing 8 with a housing cover 10.
  • An input and an output axis 12, 14 of the rotors 2, 4 are set to each other.
  • Adjacent teeth 16, 18 of the face gear 6 each define a working space 19 which receives fluid from an inlet channel 20 and a low pressure area 20 and increases pressure after a rotation of the rotors 2, 4 to an output channel 22 and high-pressure region 22 outputs.
  • the working space 19 has the largest volume on the input channel 20, which decreases in the rotation of the rotors 2, 4 to the output channel 22 and then increased again to the input channel 20.
  • the work spaces 19 connected to the input channel 20 form the so-called suction side and the work spaces 19 connected to the outlet channel 22, the so-called pressure side of the delivery unit 1.
  • the housing cover 10 has a radially recessed cylinder portion 23 which dips into the housing 8. An annular surface 24 of the housing cover 10 formed by the grading bears against a likewise annular housing end face 25 of the housing 8 without play. With fasteners 26, such as screws, the housing cover 10 is sealingly connected to the housing 8.
  • the drive rotor 2 further has a drive pin 28 which is mounted radially in a through hole 29 of the housing 8 and led out with a pin end portion 30 of the housing. At the pin end portion 30 of the drive rotor 2 is driven by an actuator, such as an electric motor.
  • the output rotor 4 is mounted with a driven pin 32 in a bearing recess 33 of the cylinder portion 24 of the housing 8 radially slidably.
  • the teeth 16 of the output rotor 4 are annularly formed on a cylindrical support portion 34 which is also slidably mounted with its lateral surface 35 in the housing 10. Furthermore, the driven rotor 4 is supported on a bearing shell section 37 of the drive rotor 2 with a ball section 36 extending centrally from the carrier section 33. A side facing away from the working spaces 19 spherical shell-shaped rear support surface 38 of the bearing shell portion 36 is slidably mounted in the housing 8. Accordingly, a side facing away from the working spaces 19 and back annular support surface 40 of the support portion 34 which extends perpendicular to the output shaft 14, frontally mounted on the cylinder portion 24 of the housing cover 10 sliding and backlash.
  • the teeth 18 of the drive rotor 2 are annularly formed on a frusto-conical annular surface 43 of the bearing shell portion 37 and extend around the ball portion 36 of the output rotor 4 around.
  • the passage opening 29 of the housing 8 is sealed with a sealing ring 44 to the outside.
  • a first and second pressure pocket 48, 50 are provided, which act on the support surfaces 38, 40 of the rotors 2, 4 with support pressure.
  • the first pressure pocket 48 which acts on the drive rotor 2 with support pressure, extends in a circle-shaped manner about the drive axis 12 and is bounded radially by an inner and an outer support web 52, 54.
  • the second pressure pocket 50 is arranged in a circle segment around the output shaft 14 and is also bounded radially by an inner and outer support web 56, 58.
  • the first pressure pocket 48 is in fluid communication with the outlet channel 22.
  • the high pressure groove 59 extends in the cutting plane in FIG. 1 through the outer support rib 54 therethrough.
  • the introduced in the housing cover 10 pressure pocket 50 is connected via a second and third high-pressure groove 60, 61 also with the output channel 22 of the delivery unit 1 in fluid communication.
  • the second high pressure groove 60 extends radially from the pressure pocket 50 through the outer support rib 58 and terminates in the third high pressure groove 61, which runs parallel to the output shaft 14 in the housing 8 along the cylinder portion 24 of the housing cover 10 and the output rotor 4 to the output channel 22 ,
  • the pressure in the pressure pockets 48, 50 thus corresponds approximately to the fluid pressure in the outlet channel 22.
  • the pressure pockets 48, 50 have a concentric extent about the respective input and output axes 12, 14 of, for example 60 ° in the plane of the FIG. 1 into and 60 ° out of the drawing plane. Thus, these are arranged substantially opposite to the high fluid pressure working spaces 19 and can counteract the resulting pressure forces.
  • a first and second pressure engagement surfaces 62, 63 of the fluid pressure in the pressure pockets 48, 50 on the rotors 2, 4 are each in size to a third and fourth pressure application surface 64, 65 of the fluid pressure of the working chambers 19 adapted to the rotors 2, 4.
  • the third pressure application surface 64 of the output rotor 4 essentially consists of the region which lies outside the sphere section 36 and in the high-pressure region of the working chambers 19.
  • the fourth pressure application surface 65 On the drive rotor 2 is the fourth pressure application surface 65 and substantially corresponds to the part of the annular surface 43, which is located in the region of high fluid pressure of the working chambers 19.
  • the configuration of the size of the first pressure application surface 62 is such that the proportions of the respective forces resulting from the acting on the first and on the third pressure application surface 62, 64 fluid pressure, which are oppositely directed, are approximately equal.
  • the respective rotor 2, 4 is thus approximately in a hydrostatic equilibrium by the attacking surfaces 62, 63, 64, 65 acting thereon approximately in the region of the high fluid pressure of the working spaces 19.
  • the surface 62 to 65 may be configured such that they are substantially equal.
  • the 120 ° extension about the input and output axes 12, 14 and the geometry of the pressure pockets 48, 50 is only a guide and can be varied as desired, depending on the application of the delivery unit 1 minimum bearing forces, minimum surface pressure between the rotors. 2 , 4 and the housing 8 and to achieve an optimal hydrostatic balance of the rotors 2, 4.
  • the output rotor 4 has, in addition to the pressure pocket 50, an end-side support space 66, in order, inter alia, to minimize the acting bearing forces. This is bounded by a recess of the housing cover 10 and by a rear end face 68 of the output pin 32.
  • the support space 66 is connected via a first, second and third Niederbuchnut 70, 72, 74 with the input channel 20 of the delivery unit 1.
  • the first low-pressure groove 70 extends parallel to the output shaft 14 along the bearing recess 33 of the housing cover 10 to the support surface 40 of the output rotor 4 and opens into the second Niederdrucknut 72.
  • annular chamber 76 For leakage return is in the region of the drive pin 28, in particular of the region of the sealing ring 44, an annular chamber 76 is inserted into the housing 8, which is connected to the input channel 20.
  • the annular chamber 76 is bounded by a recess in the housing 8, by the sealing ring 44 and the driven pin 32.
  • the connection of the annular channel 76 with the input channel 20 via a connecting groove 78, which substantially in the plane in FIG. 1 is introduced in the housing 8 and extends along the drive rotor 2 between the annular channel 76 and the input channel 20.
  • an annular groove 79 is inserted into the housing 8.
  • a pressure application surface 80 of the fluid pressure in the annular groove 79 on the drive rotor 2 essentially corresponds to the end face 68, which serves as a pressure application surface for the fluid pressure in the support space 66.
  • FIG. 2 shows a longitudinal section through a delivery unit 1 according to a second embodiment, in which the pressure pockets 48, 50, the support space 66 and the annular chamber via bores with the input and output channels 20, 22 are connected.
  • the fluid connection of the drive rotor 2 associated pressure pocket 48 with the output channel 22 via a first and second high-pressure bore 81, 82.
  • These are introduced into the housing 8, wherein the first high-pressure bore 81 from the pressure pocket 48, away from the support surface 38, to to the second high pressure bore 82 extends, which is obliquely introduced to the output channel 22.
  • the first high pressure bore 81 is in the production in the unassembled state from an inner region of the housing 8 and the second drivable from the output channel 22 from.
  • the pressure pocket 50 is connected via a third and fourth high-pressure bore 84, 86 with the output channel 22.
  • the third high-pressure bore 84 also passes through the housing 8 at an angle to the outlet channel 22 and opens into the fourth high-pressure bore 86, which is introduced obliquely to the output axis 14 into the cylinder section 24 of the housing cover 10 up to the pressure pocket 50.
  • the third high-pressure bore 84 like the first high-pressure bore 81, is drilled from an inner region of the housing 8 and the fourth high-pressure bore 86 is simply drilled into the outer circumferential surface of the cylinder portion 24.
  • the support space 66 is in fluid communication with the input passage 20 via first and second low pressure bores 88, 90.
  • the first low-pressure bore 88 passes through the cylinder portion 24 of the housing cover 10 obliquely to the output shaft 14 toward the input channel 20 and merges into the second low-pressure bore 90 also extending obliquely through the housing 8, which opens in the inlet channel 20.
  • the production takes place once at the second low-pressure bore 90 from the inner region of the housing 8 and at the first low-pressure bore 88 from the outer lateral surface of the cylinder section 24.
  • the annular channel 76 is in fluid communication with the support space 66 via bores introduced in the rotors 2, 4.
  • a first connection bore 92 extends completely and approximately coaxially with the output axis 14 through the output rotor 4.
  • the ball portion 36 of the output rotor 4 is slightly flattened at its apex, whereby a connecting space 94 between the ball portion 36 and the bearing shell portion 37 of the drive rotor 2 is formed.
  • a second connecting bore 96 is introduced as a blind hole in the drive rotor 2 approximately coaxially to the drive shaft 12 and ends approximately in the region of the annular channel 76.
  • This connecting bore 96 is then connected via an introduced in the drive rotor 2 radial bore 98 with the annular channel 76.
  • Between the passage opening 29 and the drive pin 28 of the drive rotor 2 is a small gap 100, via which the annular groove 79 is in fluid communication with the annular chamber 76 and thus the pressure application surface 80 is acted upon by fluid pressure.
  • All holes 81, 82, 84, 86, 88, 90, 92, 96, 98 are arranged in the delivery unit 1, that they are easily manufacturable and may well deviate from the arrangement described above.
  • the input and output rotors serve to convert fluid pressure of the pressure medium volume flow into mechanical energy.
  • the drive rotor can then drive, for example, a generator.
  • a hydraulic motor is well known from the prior art, which is why at this point will not be discussed in more detail.
  • the advantageous features of the delivery unit 1 according to the invention apply correspondingly to the hydraulic motor.
  • a hydraulic machine 1 with a drive rotor 2 and an output rotor 4, the axes 12, 14 are employed to each other and interacting via a spur gear toothing 6.
  • a working space 19 is bounded in each case, which can be connected to an inlet channel 20 and an outlet channel 22 during rotation of the rotors.
  • a rear support surface 38 of a rotor 2 facing away from the work spaces 19 can be acted upon by a support pressure corresponding to a pressure in the work spaces 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
EP20090006163 2008-05-14 2009-05-06 Hydromachine Withdrawn EP2119869A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810023475 DE102008023475A1 (de) 2008-05-14 2008-05-14 Hydromaschine

Publications (1)

Publication Number Publication Date
EP2119869A2 true EP2119869A2 (fr) 2009-11-18

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ID=40874640

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20090006163 Withdrawn EP2119869A2 (fr) 2008-05-14 2009-05-06 Hydromachine

Country Status (2)

Country Link
EP (1) EP2119869A2 (fr)
DE (1) DE102008023475A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011117087A3 (fr) * 2010-03-26 2013-02-14 Robert Bosch Gmbh Unité de refoulement
WO2013057112A3 (fr) * 2011-10-19 2014-03-20 Robert Bosch Gmbh Unité de transport
US9670778B2 (en) 2012-04-25 2017-06-06 Robert Bosch Gmbh Rotary piston engine which acts as a pump, condenser or motor for a fluid

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004026048A1 (de) 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Spaltverluststromsteuerung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004026048A1 (de) 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Spaltverluststromsteuerung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011117087A3 (fr) * 2010-03-26 2013-02-14 Robert Bosch Gmbh Unité de refoulement
WO2013057112A3 (fr) * 2011-10-19 2014-03-20 Robert Bosch Gmbh Unité de transport
US9422935B2 (en) 2011-10-19 2016-08-23 Robert Bosch Gmbh Feed unit
US9670778B2 (en) 2012-04-25 2017-06-06 Robert Bosch Gmbh Rotary piston engine which acts as a pump, condenser or motor for a fluid
CN104246130B (zh) * 2012-04-25 2017-08-25 罗伯特·博世有限公司 作为用于流体的泵、压缩机或马达的旋转活塞机

Also Published As

Publication number Publication date
DE102008023475A1 (de) 2009-11-19

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