EP0578005B1 - Geräuschgedämpfte hydrostatische Verdrängermaschine - Google Patents

Geräuschgedämpfte hydrostatische Verdrängermaschine Download PDF

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Publication number
EP0578005B1
EP0578005B1 EP93109492A EP93109492A EP0578005B1 EP 0578005 B1 EP0578005 B1 EP 0578005B1 EP 93109492 A EP93109492 A EP 93109492A EP 93109492 A EP93109492 A EP 93109492A EP 0578005 B1 EP0578005 B1 EP 0578005B1
Authority
EP
European Patent Office
Prior art keywords
ring
pressure
cylinder block
lift ring
retaining rings
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93109492A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0578005A1 (de
Inventor
Gerhard Fähnle
Günther Nagel
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.)
JM Voith GmbH
Original Assignee
JM Voith 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 JM Voith GmbH filed Critical JM Voith GmbH
Publication of EP0578005A1 publication Critical patent/EP0578005A1/de
Application granted granted Critical
Publication of EP0578005B1 publication Critical patent/EP0578005B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders

Definitions

  • the present invention relates to a noise-damped hydrostatic displacement machine according to the preamble of the claim.
  • a noise-damped hydrostatic displacement machine of this type is known from DE-OS 39 21 790.
  • the essence of this hydrostatic displacement machine is to seal the - in relation to the cam ring - the radially outer area with respect to the radially inner area and to apply it with different pressure so that the noise level caused by the position of the cam ring is reduced.
  • DE-GM 84 07 367 show displacement elements (FIG. 1, part 17 or FIG. 1, part 16) which, viewed axially, are guided on the lifting ring (14 or 20) via two retaining rings (33, 34 or 26, 27).
  • DE-AS 24 30 119 shows a radial seal (grooves in the cam ring) between the cam ring and retaining ring ( Figure 1).
  • the invention has for its object to provide a hydrostatic displacement machine according to the preamble of claim 1, in which despite high tolerances, the required tightness between the radially outer and the radially inner region can be achieved.
  • a drive shaft 13 is mounted in this (see also roller bearing 14 and drive shaft seal 15).
  • the drive shaft 13 is connected by means of a clutch 16 to a cylinder block 17, which in turn is rotatably mounted on the control pin 11.
  • a cylinder block 17 In the cylinder block 17 there are, in a star-shaped arrangement, several, for example seven, pistons 18; each of these pistons 18 is in turn articulated to a piston shoe 19. (These functional units consisting of the piston 18 and the piston shoe 19 form so-called displacement elements, the circulation of which causes the actual pump effect).
  • a cam ring 20 is arranged in the housing 10 and assumes an eccentric position relative to the control pin 11 (cf. eccentricity "e").
  • the piston shoes 19 slide when the cylinder block 17 rotates along the inner circumferential surface of this cam ring 20.
  • the size of the eccentricity e between the control pin 11 and the cam ring 20 can be changed, namely by displacing the cam ring 20 with the aid of actuating pistons 21 and 22; These actuating pistons 21/22 are adjusted accordingly to the required pump output by means of a pressurization by means of liquid.
  • a low-pressure channel 23 and a high-pressure channel 24 extend through the housing 10 and through the control pin 11.
  • the region 25 of the housing interior located radially inside the cam ring 20, in which the drive shaft 13, the roller bearing 14, the clutch 16, the cylinder block 17 and the piston 18 with the piston shoe 19 circulate, is connected via a leak oil channel 29 to a low-pressure area, for example to a - symbolically represented - unpressurized oil container 9. There is therefore a pressure in this radially inner region 25, which is approximately between 0 and 1 bar.
  • the region 26 of the housing interior located radially outside of the stroke ring 20 is separated from the rest of the housing interior, i.e. sealed from the radially inner region 25 in that an annular groove is provided in one of the end faces of the cam ring 20, in which an axially displaceable sealing ring is located.
  • at least one elastic element e.g. an O-ring
  • the cam ring on the one hand and the sealing ring on the other hand are spread apart in the axial direction.
  • the cam ring 20 always lies with its one end face in a sealing manner on the surface 40 of the housing 10, while on the opposite end face of the cam ring 20 the sealing ring is constantly in sealing contact with the area 41 of the housing cover 12.
  • a "mean" pressure of approx. 2 to 4 bar builds up in the radially outer region 26 of the interior, which e.g. can thereby occur that leakage liquid penetrates from a pressure chamber and that along the actuating piston 21 into the outer region 26.
  • the outer region 26 is connected to any pressure source via a channel 33, so that the "average" pressure in the region 26 mentioned can be built up as quickly as possible.
  • the outer region 26 is connected to the leakage oil channel 29 via bores.
  • a check valve 37 is arranged in the connection between the outer region 26 and the leak oil channel 29, which only opens when the pressure difference mentioned exceeds the desired value. (Instead of the check valve 37, any other suitable pressure valve, for example a pressure relief valve, can also be provided).
  • the housing 10 has on its inside in a known manner two guide surfaces 42 for guiding the cam ring 20. Through this guide surface 42, the radially outer region 26 of the housing interior is divided into two chambers, which are however connected to one another via channels 45.
  • the connecting channels 45 are incorporated in the housing 10; Similar connection channels could, however, also be provided in the cam ring 20.
  • FIG. 1 a connecting channel 33 'from the low-pressure channel 23 to one of the connecting channels 45 is also shown with dash-dotted lines.
  • This arrangement is to be regarded as an alternative to the above-mentioned channel 33 (cf. FIG. 2) and comes into question if there is a "medium" liquid pressure in the low-pressure channel 23, which is now in the area 26 located radially outside the cam ring reproduces the interior of the housing.
  • the radial piston pump drawn and described so far is state of the art.
  • the object of the present invention relates to the seal between the inner and outer regions 25 and 26, respectively, starting from the cam ring 20 per se.
  • FIG. 1 The concept or construction according to the invention with regard to the sealing which is improved compared with the prior art is shown in FIG.
  • a seal is integrated between the inner region 25 and the outer region 26 on both sides of the cam ring 20, i.e. the seal drawn with reference to FIG. 3 between the cam ring 20 and the housing 10 is provided in mirror image equally between the cam ring 20 and the housing cover 12.
  • a flange-like (see reference numeral 30 ') so-called retaining ring 30 is provided on both sides of the cam ring 20, which - related on the cam ring 20 - can be axially spread relative to each other.
  • the sealing by means of the retaining rings 30 is designed as follows: the lifting ring 20 has a first recess on both sides, into which the retaining rings 30 are fitted via their flange extension 30 '; the cam ring 20 also has a second recess, so that a radial gap 31 is formed between the cam ring 20 and the retaining ring 30, into which an elastic seal, e.g. in the form of an O-ring.
  • the deformation of the O-ring in the radial intermediate space 31 now takes place radially and no longer axially, as in the prior art, so that the manufacturing process no longer requires too much effort with regard to the tolerances of the longitudinal dimensions.
  • the installation of two retaining rings 30 and thus two sealing washers also has the advantage that not only can the longitudinal tolerances be compensated, but also angular deviations between the cam ring 20 and the housing 10 or the housing cover 12, as well as changes in the angle of the cam ring 20 due to load-dependent deformations can be compensated.
  • the retaining rings are required for the basic function of the pump anyway, they hold the sliding blocks 18 on the running surface of the retaining ring 20.
  • the specific pairing cam ring 20 / retaining ring 30 is designed or designed so that the slightly increased internal pressure P 1 (of the space above the cam ring 20) up to the seal (O-rings) in the radial space 31 acts fully on the retaining ring 30 and on which Housing 10 facing side of the retaining ring 30, the conjugate pressure Pi decreases to the level of the interior.
  • the corresponding contact pressure F1 or F2 results in a resulting defined contact pressure Fan for pressing the retaining rings 30 against the housing 10 (or on the housing cover 12).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Sealing Devices (AREA)
  • Jet Pumps And Other Pumps (AREA)
EP93109492A 1992-06-19 1993-06-15 Geräuschgedämpfte hydrostatische Verdrängermaschine Expired - Lifetime EP0578005B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4220028A DE4220028C1 (enrdf_load_stackoverflow) 1992-06-19 1992-06-19
DE4220028 1992-06-19

Publications (2)

Publication Number Publication Date
EP0578005A1 EP0578005A1 (de) 1994-01-12
EP0578005B1 true EP0578005B1 (de) 1995-05-31

Family

ID=6461338

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93109492A Expired - Lifetime EP0578005B1 (de) 1992-06-19 1993-06-15 Geräuschgedämpfte hydrostatische Verdrängermaschine

Country Status (7)

Country Link
US (1) US5394787A (enrdf_load_stackoverflow)
EP (1) EP0578005B1 (enrdf_load_stackoverflow)
JP (1) JPH0666250A (enrdf_load_stackoverflow)
AT (1) ATE123328T1 (enrdf_load_stackoverflow)
DE (1) DE4220028C1 (enrdf_load_stackoverflow)
DK (1) DK0578005T3 (enrdf_load_stackoverflow)
ES (1) ES2073319T3 (enrdf_load_stackoverflow)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4440282A1 (de) * 1994-11-11 1996-05-15 Aladar Roth Hydraulische Kolbenmaschine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2238952A1 (de) * 1972-08-08 1974-02-28 Bosch Gmbh Robert Radialkolbenmaschine
DE2430119C3 (de) * 1974-06-22 1980-12-04 Voith Getriebe Kg, 7920 Heidenheim Hydrostatische Radialkolbenmaschine
DE3001381A1 (de) * 1980-01-16 1981-07-23 Robert Bosch Gmbh, 7000 Stuttgart Hydrostatische maschine
JPS57168069A (en) * 1981-04-07 1982-10-16 Hitachi Constr Mach Co Ltd Radial piston type pump motor
DE8407367U1 (de) * 1984-03-10 1985-07-04 Robert Bosch Gmbh, 7000 Stuttgart Radialkolbenmaschine (Pumpe oder Motor)
DE3700573A1 (de) * 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
DE3921790A1 (de) * 1989-07-03 1991-01-17 Voith Gmbh J M Hydrostatische verdraengermaschine

Also Published As

Publication number Publication date
EP0578005A1 (de) 1994-01-12
ATE123328T1 (de) 1995-06-15
JPH0666250A (ja) 1994-03-08
DK0578005T3 (da) 1995-10-02
ES2073319T3 (es) 1995-08-01
DE4220028C1 (enrdf_load_stackoverflow) 1993-06-24
US5394787A (en) 1995-03-07

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