US3813194A - Hydraulic vane machine with controlled vanes - Google Patents

Hydraulic vane machine with controlled vanes Download PDF

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Publication number
US3813194A
US3813194A US00303633A US30363372A US3813194A US 3813194 A US3813194 A US 3813194A US 00303633 A US00303633 A US 00303633A US 30363372 A US30363372 A US 30363372A US 3813194 A US3813194 A US 3813194A
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United States
Prior art keywords
vane
throttle
pair
rotor
valve seat
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
US00303633A
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English (en)
Inventor
J Scholz
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.)
Bosch Rexroth AG
Original Assignee
GL Rexroth 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 GL Rexroth GmbH filed Critical GL Rexroth GmbH
Application granted granted Critical
Publication of US3813194A publication Critical patent/US3813194A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • the present invention relates to vane machines such as a vane pump or vane motor.
  • vane machines such as a vane pump or vane motor.
  • the high pressure conduits and low pressure conduits are reliably sealed from each other. This requires a tight engagement of the outer ends of the vanes with the inner surface of the surrounding cam ring, particularly in the zone in which the expanding intervane spaces begin to contract, and which is located between the inlet and outlet ports.
  • Another object of the invention isto exert only little pressure on the vanes moving along the inlet and outlet ports of the hydraulic vane machine, but being pressed by a suitable pressure against the eccentric cam ring in the region between the ends of the inlet and outlet ports.
  • Another object of the invention is to avoid that excessive pressure is suddenly applied to a vane'moving from a low pressure port to a high pressure port.
  • the present invention provides a flow through a first throttle into a bottom chamber of a valve slot, and from there through a second throttle to a region of lower pressure.
  • the intermediate pressure acting in the bottom chamber of the vane slot and on the vane can be exactly detennined.
  • the right pressure in the bottom chamber acting on the vane can be obtained.
  • the bottom chamber in each vane slot is connected by a throttle with the leading and trailing intervane spaces, and the flow cross section of each throttle is influenced and varied by a valve element operated by the pressure of the fluid passing through the throttles.
  • the communication between the bottom chamber with the intervane spaces trailing and leading the respective vane has the advantage that in the intervane space in which the lower pressure prevails, the pressure rises in the intermediate zone before the respective intervane space enters the region where the high pressure of the vane machine prevails. In this manner, the noise level of the hydraulic vane machine, and also the pressure drop between the respective intervane space and the pressure zone, which influences the wear, can be reduced.
  • the throttles are mounted in bores in the rotor, and have valve seats cooperating with valve elements in the form of spherical balls.
  • the valve seat has one or several transverse channels which form a throttle having a smaller cross section than the main throttling passage.
  • FIG. 1 is a fragmentary, partly schematic, plan view, partially in section, illustrating a hydraulic vane machine including a preferred embodiment of the invention.
  • FIG. 2 is a fragmentary horizontal plan view illustrating a detail of FIG. 1 on an enlarged scale.
  • a rotor 1 is surrounded by an eccentric cam ring 2 whose center is spaced the distance e from the axis A of rotor 1.
  • An arrow 6 indicates the direction of rotation of rotor 1.
  • a stationary valve plate 3 has two partcircular control ports 4 and 5, and it can be assumed that control port 4 is a suction port, and control port 5 is a pressure port.
  • the ends 5a and4b of the ports 4 and5 are spaced from each other, and the ends 4a and 5b of the'ports 4 and 5 are also spaced from each other so that two diametrically opposite intermediate zones 13 are formed between the ports 4 and 5.
  • Rotor 1 has substantially radial uniformly circumferentially spaced vane slots which are schematically shown, except for three vane slots 7', 7' and 7".
  • Vanes 8, 8 and 8" are located in the respective vane slots 7, 7 and 7", projecting outward from the outer surface of rotor 1 and having outer ends 8a, 8a, formed by two slanted faces 8n' and 8v.
  • the inner ends 8f of the vanes form rounded bottom chambers 7a at the radially inner ends of the vane slots 7, 7' and 7".
  • the inner surface of cam ring 2, the outer surface of rotor l, and adjacent vanes form intervane spaces, for example the leading intervane space 12', and the trailing intervane space 10 located on opposite sides of a vane 8'.
  • each vane slot 7 is connected by a bore 9, for example by bore 9', with the trailing intervane space 10', and by a bore 1], for example bore 11' with an intervane space 12, for example the leading intervane space 12.
  • the respective bores 9 and 11 Adjacent the intervane spaces, the respective bores 9 and 11 are threaded for holding threaded throttle bodies 9b, 11b each of which has a passage 20, as best seen in FIG. 2.
  • the throttle bodies 9b, 11b have at the inner ends thereof, frustro-conical valve seats 90, 110 which cooperate with spherical balls 21 movable in the inner end portions of the bores 9, 9.
  • the ball 21 in bore 11 is shown spaced from the valve seat, and the ball 21 in bore 9' is shown abutting the valve seat due to the flow of fluid from intervane space 12' to intervane space 10'.
  • transverse throttling channels 9d, 11d are provided, which, when closed by a ball 29 abutting the respective valve seat, form throttle passages whose total cross section is smaller than the cross section of the throttle passages 20.
  • the leading intervane space 12' in the intermediate zone 13 between the end 4b of the suction port 4, and the opposite end a of the pressure port 5 is in communication with the pressure port 5 so that the respective leading intervane space 12' contains pressure fluid at high pressure.
  • the intervane space which trails the vane 8' is still in communication with the low pressure suction port 4 through the port end 46.
  • fluid flows through throttle passage of the throttle body 11b secured in the bore 11, and presses the respective valve element 21 away from the respective valve seat 11c.
  • the fluid flows then through bottom chamber 7a and into the inner end of bore 77, exerting pressure on valve element 21 to abut valve seat 9c, see also FIG. 2, flowing through the throttle channels 9d and through the respective throttle passage 21 into the intervane space 10' so that fluid flows from the high pressure port end 5a to the low pressure port end 4b.
  • the magnitude of the pressure in the bottom chamber 7a acting on the inner end face 8]" of the respective vane 8' is determined by the difference between the effective throttling cross section.
  • the difference between the cross section of throttle passage 20 and the total cross section of all throttling channels 9d determines the pressure in the bottom chamber 70'. The greater the difference is, the greater is the pressure in bottom chamber 7a, and also acting on vane 8.
  • leading and trailing intervane spaces 10, 12 are placed in the region of the suction port 4 during further rotation of the rotor, via pressure acting on vane 8' is again balanced.
  • the invention is not limited to the disclosed embodiment, and the throttling passages and channels for determining the pressure acting on the inner ends 8f of the vanes, can also be provided in control valve plates.
  • Hydraulic vane machine with pressure controlled vanes comprising a rotor having a plurality of vane slots; vanes movably mounted in said vane slots and having outer ends projecting from said rotor and inner ends forming bottom chambers in said vane slots; an actuating cam ring surrounding said rotor eccentrically to the axis of said rotor and being engaged by said outer ends of said vanes so that expanding and contracting intervane spaces are formed between said rotor, said cam ring, and pairs of adjacent vanes; a pair of throttle means mounted on said rotor for each vane and having a pair of first ends communicating with said bottom chamber of the respective vane slot, and a pair of second ends; and means for applying different pressures at said second ends and connecting said second ends of each pair of throttle means with a pair of intervane spaces leading and trailing the respective vane, respectively, whereby at different pressuresin the intervane spaces of the respective pair, fluid flows through the respective pair of throttle means and through the respective bottomchamber whereby the respective
  • each throttle means includes a throttle passage having a valve seat at said first end, and a valve element cooperating with the respective valve seat for partly closing the respective throttle passage so that fluid flowing through said throttle passages urges one of said valve elements of a pair of throttle means away from the valve seat thereof, and the other valve element against the seat thereof so that the flow of fluid through the respective throttle passage and thereby through the respective pair of throttle means and through the respective bottom chamber is reduced.
  • each valve seat is formed with at least one channel communicating with the respective throttle passage and remaining open when the respective valve element is pressed against the valve seat thereof; and wherein the flow cross section of said channel is less than the flow cross section of the respective throttle passage.
  • each valve seat is formed with a plurality of channels; and wherein the total flow cross section of all channels of each valve seat is less than the flow cross section of the respective throttle passage.
  • Hydraulic vane machine as claimed in claim 4, wherein said channels are transverse to the respective throttle passage; and wherein said valve elements are spherical balls.
  • each throttle means includes a throttle passage having a valve seat at said first end, and a valve element cooperating with the respective valve seat for partly closing the respective throttle passage so that fluid flowing through said throttle passages urges one of said valve elements of a pair of throttle means away from the valve seat thereof, and the other valve element against the seat thereof so that the flow of fluid through the respective throttle passage and thereby through the respective pair of throttle means and through the respective bottom chamber is reduced.
  • Hydraulic vane machine as claimed in claim 1, comprising stationary means including two substantially semicircular ports for high pressure fluid and low pressure fluid having two pairs of circumferentially spaced port ends forming between each other two diametrically positioned intermediate zones; and wherein said vanes are circumferentially spaced such equal dis tances that intervane spaces leading and trailing a vane located in the middle of an intermediate zone communicate with said ports, respectively, whereby different pressures prevail at said second ends of the respective pair of throttle means so that the pressure in the respective bottom chamber is intermediate said different pressures.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US00303633A 1971-11-20 1972-11-03 Hydraulic vane machine with controlled vanes Expired - Lifetime US3813194A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2157637A DE2157637C3 (de) 1971-11-20 1971-11-20 Flügelzellenpumpe oder -motor

Publications (1)

Publication Number Publication Date
US3813194A true US3813194A (en) 1974-05-28

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ID=5825662

Family Applications (1)

Application Number Title Priority Date Filing Date
US00303633A Expired - Lifetime US3813194A (en) 1971-11-20 1972-11-03 Hydraulic vane machine with controlled vanes

Country Status (3)

Country Link
US (1) US3813194A (de)
JP (1) JPS4863304A (de)
DE (1) DE2157637C3 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6527525B2 (en) * 2000-02-08 2003-03-04 Thomas E. Kasmer Hydristor control means
US20050036897A1 (en) * 2003-08-11 2005-02-17 Kasmer Thomas E. Rotary vane pump seal
US20060059904A1 (en) * 2004-09-23 2006-03-23 Alper Shevket Hydraulic traction system for vehicles
CN114183341A (zh) * 2021-07-03 2022-03-15 江苏湖润泵业科技有限公司 一种具有内凹式叶片的叶片泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5452710U (de) * 1977-09-20 1979-04-12
DE3815791A1 (de) * 1987-07-22 1989-02-02 Georg Foerg Verbesserung des fluegelzellenprinzips

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809593A (en) * 1953-07-21 1957-10-15 Vickers Inc Power transmission
US3102493A (en) * 1961-02-10 1963-09-03 American Brake Shoe Co Pressure balanced vane
US3451346A (en) * 1967-11-14 1969-06-24 Sperry Rand Corp Power transmission
US3516768A (en) * 1968-11-01 1970-06-23 Sperry Rand Corp Power transmission
US3598510A (en) * 1969-02-27 1971-08-10 Komatsu Mfg Co Ltd Vane pump
US3627456A (en) * 1970-03-25 1971-12-14 Diversified Prod Vanes for fluid power converter

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2719512A (en) * 1951-03-15 1955-10-04 Pixley Truck Sales Company Power transmitting devices

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809593A (en) * 1953-07-21 1957-10-15 Vickers Inc Power transmission
US3102493A (en) * 1961-02-10 1963-09-03 American Brake Shoe Co Pressure balanced vane
US3451346A (en) * 1967-11-14 1969-06-24 Sperry Rand Corp Power transmission
US3516768A (en) * 1968-11-01 1970-06-23 Sperry Rand Corp Power transmission
US3598510A (en) * 1969-02-27 1971-08-10 Komatsu Mfg Co Ltd Vane pump
US3627456A (en) * 1970-03-25 1971-12-14 Diversified Prod Vanes for fluid power converter

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6527525B2 (en) * 2000-02-08 2003-03-04 Thomas E. Kasmer Hydristor control means
US20050036897A1 (en) * 2003-08-11 2005-02-17 Kasmer Thomas E. Rotary vane pump seal
US7484944B2 (en) 2003-08-11 2009-02-03 Kasmer Thomas E Rotary vane pump seal
US20060059904A1 (en) * 2004-09-23 2006-03-23 Alper Shevket Hydraulic traction system for vehicles
US7331411B2 (en) * 2004-09-23 2008-02-19 Alper Shevket Hydraulic traction system for vehicles
CN114183341A (zh) * 2021-07-03 2022-03-15 江苏湖润泵业科技有限公司 一种具有内凹式叶片的叶片泵

Also Published As

Publication number Publication date
JPS4863304A (de) 1973-09-03
DE2157637B2 (de) 1980-08-07
DE2157637A1 (de) 1973-05-24
DE2157637C3 (de) 1981-05-27

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