US20150198156A1 - Control ring for a hydrostatical device - Google Patents

Control ring for a hydrostatical device Download PDF

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Publication number
US20150198156A1
US20150198156A1 US14/571,413 US201414571413A US2015198156A1 US 20150198156 A1 US20150198156 A1 US 20150198156A1 US 201414571413 A US201414571413 A US 201414571413A US 2015198156 A1 US2015198156 A1 US 2015198156A1
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US
United States
Prior art keywords
control ring
openings
axial
balance
opening
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.)
Abandoned
Application number
US14/571,413
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English (en)
Inventor
Christer Odenmarck
Jonas Forssell
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.)
Moog GmbH
Original Assignee
Volvo Car Corp
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 Volvo Car Corp filed Critical Volvo Car Corp
Assigned to VOLVO CAR CORPORATION reassignment VOLVO CAR CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FORSSELL, JONAS, Odenmarck, Christer
Publication of US20150198156A1 publication Critical patent/US20150198156A1/en
Assigned to MOOG GMBH reassignment MOOG GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VOLVO CAR CORPORATION
Abandoned 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
    • 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
    • F04C2/102—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 the two members rotating simultaneously around their respective axes
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C14/14—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves

Definitions

  • the present disclosure relates to displacements pumps and especially a control ring for a displacement pump.
  • the port plate is provided with a first and a second opening, which are adapted to correspond to a first and a second pressure chamber of a displacement pump. By turning the port plate, the displacement of the displacement pump can be controlled.
  • a problem with the port plate according to the prior art is that the port plate becomes a large diameter due to its pressure balance areas outside the control openings. Another problem is to seal the port plate sufficiently to avoid leakage in the control interface.
  • An object of the present disclosure is to provide an inventive control for displacement pumps, with which previously mentioned problems are avoided.
  • a control ring for controlling the flow of a pressure medium in a displacement pump.
  • the control ring is centred about a rotational axis about which it extends.
  • the control ring is further provided with a first and a second axial surface, an inner and an outer diameter and thereby an inner and outer radial surface.
  • the first axial surface is provided with an interface section having at least a first and a second opening.
  • the first and second openings are separated by a first and a second intermediate section, also called land.
  • one of the openings is a high pressure opening.
  • the high pressure opening can be any of the two openings, and can also change depending on if the displacement pump is driven as a motor or as a pump.
  • the first and second openings mouth or open to a corresponding mouthing area provided at either of the inner and outer radial surface.
  • An advantaged of the radial placement of the mouthing of the openings is that it permits pressure equilibrium around the axial surfaces of the control ring.
  • first and the second openings are diverted about 90 degrees to a radial surface, an easy connection of input and output conduits are facilitated.
  • control ring is provided with at least a first balance area at the second radial surface.
  • the balance area is supposed to balance the pressure forces between the first and the second axial surfaces, whereby the balance area is arranged opposite the opening it balances.
  • the balance area is interconnected with one of the first and second opening via pressure conduits, wherein the opening the balance area is connected to is the high pressure opening. Due to the connection between the opening and the balance area, the axial surface of the opening and the balance area will be subjected to the same pressure.
  • control ring is provided with at least a first and a second balance area at its second axial surface.
  • the first and the second balance area are connected to one of the first and second openings of the first axial surface area correspondently, wherein the pressure upon the balance areas corresponds to the pressure upon the surfaces in the openings.
  • An axial surface area of the at least first and second balance areas corresponds at least to an exposed axial area of the first and second openings, such that the axial force upon the first and second balance areas corresponds to the axial force upon the exposed radial areas of the first and second openings.
  • the balance areas facilitate an easy control of the control ring, due to the pressure equilibrium that is achieved between the exposed radial areas and the balance area.
  • a control ring having only one balance area interconnected with one of the first and the second opening, are preferably used just in one direction, in which the opening connected with the balance area is the high pressure opening.
  • a control ring having two balance areas each interconnected with one of the first and second openings correspondently, will have pressure equilibrium when operated either of the rotational directions.
  • the area of the pressure areas is slightly larger than the corresponding axial area of the opening it is interconnected with.
  • the first axial surface area will be pressed against a corresponding area of the pump (i.e., the rear plate or the rotor set or piston housing) it is arranged against, wherein the control ring can be sealed more efficiently.
  • the control ring can be designed such that the first opening is mouthing to the inner radial surface and the second opening is mouthing to the outer radial surface.
  • An easy connection of the first and second openings can thereby be facilitated.
  • the connection conduits can easily be separated from each other and there are no risk for leakage between the input and the output connection.
  • a configuration of the control ring such that the first opening is mouthing to the inner radial surface and the second opening is mouthing to the outer radial surface achieves an axial compact control ring, because both the openings can mouth at the same axial distances from the first axial surface.
  • the first and the second opening are mouthing to the inner radial surface, wherein the first and the second opening are mouthing to the inner radial surface at different axial distances from the first axial surface.
  • the first and second openings are mouthing to the outer radial surface, wherein the first and second openings are mouthing to the outer radial surface at different axial distances from the first axial surface.
  • seal rings are arranged such upon the outer radial surface, that the seal rings define two separate axial areas in which the first and second openings mouth respectively.
  • the seal rings are annular and coaxial with the control ring, whereby a seal ring can seal off one radial area from each other.
  • the first and/or the second opening comprises a plurality of channels.
  • first and second openings are circular arc shaped, in order to adapt to a rotating displacement pump.
  • balance valves are arranged in the first and second intermediate sections, the balance valves connect the first and second intermediate section with a mouthing area of the first and/or second opening respectively, wherein the balance valves are adapted to open if a pressure at the first or second intermediate area raises above a predetermined threshold value.
  • the control ring is adapted to be used in a displacement pump comprising a pumping unit arranged within a housing, with fix pressure sections and therewith connected supply chambers, wherein the control ring is provided between the pressure sections and the supply chambers, wherein an interface section is arranged directed towards the pressure chamber such that the control ring can be turned in order to control the flow of pressure medium.
  • FIG. 1 shows a displacement pump with a control ring according to the disclosure
  • FIGS. 2 a and 2 b show a first embodiment of a control ring according to the disclosure.
  • FIGS. 3 a and 3 b show a second embodiment of a control ring according to the disclosure.
  • FIG. 1 discloses a displacement pump 200 , in which control ring 210 is provided.
  • the displacement pump 101 is disclosed as a gerotor pump.
  • the control ring 10 , 210 is however compatible with any displacement pump having stationary pressure chambers.
  • the displacement pump 200 comprises a front and a back housing 101 , 102 , a front and a rear plate 103 , 104 , in between which a rotor set 105 is arranged, and an eccentric shaft 106 upon which the rotor set 105 and the control ring 210 are mounted.
  • the rotor set 105 is provided in between the front and the rear plates 103 , 104 , wherein the rear plate 104 is provided with supply conduits in order to connect pressure chambers of the rotor set with an inlet and an outlet 108 , 109 in the rear housing.
  • control ring 210 is provided in between the rear plate 104 and the rear housing 102 , such that it controls the flow of pressure medium between the inlet and the outlet 108 , 109 and the pressure chambers of the rotor set 105 .
  • the control ring 210 could however be arranged directly against a pumping unit, independently if it is a gerotor, bend axis pump or another displacement pump with stationary pressure chambers.
  • An actuator pin 107 is provided, which acts upon a gearing of the control ring 210 in order to rotate the control ring 210 into different control positions.
  • the control ring 110 is centred about a rotational axis ax, which also is the centre axis of the displacement pump 101 . In FIG.
  • the displacement pump 200 is provided with a control ring 210 disclosed in FIGS. 3 a and 3 b.
  • the displacement pump 200 could however also be provided with a control ring 10 disclosed in FIGS. 2 a and 2 b.
  • the only difference to the displacement pump 200 will be the configuration of the rear housing 102 , and how the inlet and the outlet 108 , 109 are connected to the control ring 10 .
  • the control ring 10 , 210 replaces a traditional port plate, wherein the displacement of the displacement pump 200 can be controlled by rotating the control ring 10 , 210 relative the rear plate 104 and thereby the pressure chambers of the rotor set 105 .
  • FIGS. 2 a and 2 b show a control ring 10 according to the disclosure.
  • the control ring having an inner radius d and an outer radius D, a first and a second axial surface 13 , 14 , and an inner and outer radial surface 11 , 12 .
  • the control ring 10 is centred about its rotational axis ax.
  • the first axial surface 13 is provided with an interface section 20 with a first and a second opening 21 , 22 .
  • the first and the second opening 21 , 22 are separated with a first and a second intermediate sections 15 , 16 .
  • the interface section 20 is adapted to connect to the pressure chambers of rotor set 105 via the rear plate 104 .
  • the first and the second opening 21 , 22 are shaped as circular arcs and follow the circumference of the control ring 10 .
  • the control ring 210 could also be arranged directly against the rotor unit 105 ; this however is mostly suitable for a device with lower pressures.
  • the first and the second opening 21 , 22 are separated by a first and a second intermediate section 15 , 16 .
  • the first and the second opening 21 , 22 are constructed by several smaller openings which all have a common upper space, such that the pressure in the whole opening 21 , 22 are the same.
  • the first opening 21 is mouthing to the inner radial surface 11 and the second opening 22 is mouthing to the outer radial surface 12 .
  • the pressure medium inlet and outlet 108 , 109 can be easily connected.
  • One of the inlet and outlet 108 , 109 is connected to the space within the inner radius of the control ring 10 ; the other is connected to the outer radial surface 12 .
  • the surface to which the second opening 22 are mouthing to is delimited by two seal rings 23 , 24 .
  • the seal rings 23 , 24 are arranged such upon the control ring 10 , that when the control ring 10 is arranged within the rear housing 102 , the seal rings 23 , 24 seals against the control ring 10 and the inner of the rear housing 102 , such that a ring formed space is formed there between.
  • the second opening 22 thereby mouth in the space in between the seal rings 23 , 24 .
  • the one of the inlet and outlet 108 , 109 that are connected to the second opening 22 thereby also mouth to the space in between the seal rings, but from the side of the rear housing 102 .
  • both the first and the second opening 21 , 22 are mouthing to their respective radial surface 21 , 22 at essentially the same axial distance from the interface surface 20 .
  • the control ring 10 is provided with a first and a second balance area 28 , 29 .
  • the balance areas 28 , 29 are interconnected with the first and the second opening 21 , 22 through a first and a second pressure conduit 26 , 27 .
  • the first and the second balance area 28 , 29 is provided with an axial surface which correspond to the axial surface of the respective first and second opening 21 , 22 . Due to the interconnection of the balance areas 28 , 29 with the corresponding openings 21 , 22 the axial pressure acting upon the first and the second balance area 24 , 25 corresponds to the pressure acting upon the axial surfaces of the first and the second opening 21 , 22 .
  • the balance areas 28 , 29 By having the same size on the balance areas 28 , 29 as the axial areas of the corresponding opening 21 , 22 , the axial forces upon the two axial sided will equal each other out.
  • the respective area of balance areas 28 , 29 are slightly larger, e.g., 4%, than the axial areas of the corresponding opening 21 , 22 .
  • the control ring 10 will thereby be pressed against the rear plate 104 , whereby a tighter seal between the control ring 10 and the rear plate 104 is achieved.
  • the control ring 10 if further provided with a gearing 6 , at which an actuator pin 107 ( FIG. 1 ) can act in order to rotate the control ring 10 relative the rear plate 104 , whereby the displacement of the displacement pump 200 can be controlled.
  • FIGS. 3 a and 3 b an alternative embodiment of the control ring 210 is disclosed.
  • the embodiment of the control ring 210 in FIGS. 3 a and 3 b is in many aspects correspondent to the control ring 10 disclosed in FIG. 2 a, b.
  • the control ring 210 is centred about its rotational axis ax and extending along the axis ax.
  • the control ring 210 having an inner and an outer diameter d, D and thereby an inner and outer radial surface 211 , 212 and is provided with a first and a second axial surface 213 , 214 .
  • the first and the second axial surface 213 , 314 is provided with an interface section 220 , with a first and a second opening 21 , 22 .
  • the first and the second opening 221 , 222 are separated by a first and a second intermediate section 215 , 216 .
  • the control ring 210 is further provided with a first and a second balance area 228 , 229 , with pressure conduits 226 , 227 , having the same functionality as the balance areas 28 , 29 and pressure conduits 26 , 27 disclosed in FIG. 1 .
  • the difference between the control ring 210 in FIGS. 3 a and 3 b and the control ring 10 in FIGS. 2 a and 2 b is where the first opening 221 is mouthing. Both the first and the second opening 221 , 222 of the control ring 210 are mouthing to the outer axial surface 212 , however at a different axial distance from the first axial surface 213 . The different axial distance of the mouthing is important in order to create two separate mouthing areas.
  • a first, a second and a third seal ring 223 , 224 , 225 is thereby also provided at the outer radial surface 212 , in order to create to mouthing spaces between the control ring 212 and the rear housing 102 .
  • the inner radial surface 211 is thereby not provided with any openings.
  • the rear housing 102 is thereby adapted to receive the control ring 210 , wherein both the pressure medium inlet and outlet 108 , 109 connected to a respective mouthing space between the control ring 210 and the rear housing 102 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
US14/571,413 2014-01-10 2014-12-16 Control ring for a hydrostatical device Abandoned US20150198156A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14150742.6A EP2894294B1 (en) 2014-01-10 2014-01-10 Control ring for a hydrostatical device
EP14150742.6 2014-01-10

Publications (1)

Publication Number Publication Date
US20150198156A1 true US20150198156A1 (en) 2015-07-16

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Application Number Title Priority Date Filing Date
US14/571,413 Abandoned US20150198156A1 (en) 2014-01-10 2014-12-16 Control ring for a hydrostatical device

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US (1) US20150198156A1 (zh)
EP (1) EP2894294B1 (zh)
CN (1) CN104776017B (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10167866B2 (en) 2014-01-10 2019-01-01 Volvo Car Corporation Displacement pump and a control ring for a displacement pump
US10968741B2 (en) 2019-02-08 2021-04-06 Volvo Car Corporation Variable pre and de-compression control mechanism and method for hydraulic displacement pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113586437B (zh) * 2021-08-20 2023-01-10 宁波开发区安德鲁精铸有限公司 一种油泵隔离板及其加工工艺

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3011447A (en) * 1956-10-01 1961-12-05 Robert W Brundage Hydraulic pump or motor
US3515496A (en) * 1968-05-06 1970-06-02 Reliance Electric Co Variable capacity positive displacement pump
EP2497950A1 (en) * 2011-03-09 2012-09-12 Volvo Car Corporation Georotor pump with capacity control valve provided rotatable within the shaft.

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334590A (en) * 1965-09-09 1967-08-08 Sperry Rand Corp Power transmission
JPH01104991A (ja) * 1986-08-27 1989-04-21 Sumitomo Electric Ind Ltd 可変容量歯車ポンプ
WO2003052272A1 (en) * 2001-12-13 2003-06-26 Performance Pumps, Llc. Improved gerotor pumps and methods of manufacture therefor
JP5084536B2 (ja) * 2008-02-05 2012-11-28 日立オートモティブシステムズ株式会社 オイルポンプ
CN203201737U (zh) * 2013-04-16 2013-09-18 意宁液压股份有限公司 手动变量双联柱塞泵

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3011447A (en) * 1956-10-01 1961-12-05 Robert W Brundage Hydraulic pump or motor
US3515496A (en) * 1968-05-06 1970-06-02 Reliance Electric Co Variable capacity positive displacement pump
EP2497950A1 (en) * 2011-03-09 2012-09-12 Volvo Car Corporation Georotor pump with capacity control valve provided rotatable within the shaft.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10167866B2 (en) 2014-01-10 2019-01-01 Volvo Car Corporation Displacement pump and a control ring for a displacement pump
US10968741B2 (en) 2019-02-08 2021-04-06 Volvo Car Corporation Variable pre and de-compression control mechanism and method for hydraulic displacement pump
US11306589B2 (en) 2019-02-08 2022-04-19 Volvo Construction Equipment Ab Mechanism and method for a high efficiency low noise hydraulic pump/motor

Also Published As

Publication number Publication date
EP2894294B1 (en) 2016-08-24
EP2894294A1 (en) 2015-07-15
CN104776017B (zh) 2018-07-03
CN104776017A (zh) 2015-07-15

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Legal Events

Date Code Title Description
AS Assignment

Owner name: VOLVO CAR CORPORATION, SWEDEN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ODENMARCK, CHRISTER;FORSSELL, JONAS;REEL/FRAME:034513/0688

Effective date: 20141211

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION

AS Assignment

Owner name: MOOG GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:VOLVO CAR CORPORATION;REEL/FRAME:051351/0562

Effective date: 20190925