US3917438A - Rotary compressor of the sliding vane type - Google Patents

Rotary compressor of the sliding vane type Download PDF

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US3917438A
US3917438A US386953A US38695373A US3917438A US 3917438 A US3917438 A US 3917438A US 386953 A US386953 A US 386953A US 38695373 A US38695373 A US 38695373A US 3917438 A US3917438 A US 3917438A
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stator
rotor
radius
transition zone
rotary compressor
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US386953A
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Rune Glanvall
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Stal Refrigeration AB
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Stal Refrigeration AB
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    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings

Definitions

  • ABSTRACT A rotary compressor of the sliding vane type, in which the vanes of the rotor slide resiliently along the inner surface of the stator the cross section profile of which defines three separate substantially circular arcs one of which has the same radius as the rotor and forms a transition zone or sealing area between the high pressure side and the low pressure side, the profile defining the inlet side or low pressure side having a radius of curvature which is greater than the mean radius of the stator and the profile defining the outlet side or high pressure side having a radius smaller than the mean radius of the stator, whereby the space between the inner surface of the stator increases continuously from substantially zero at the inlet side of the transition zone to its predetermined optimum and thereafter decreases continuously back to substantially zero at outlet side of the transition zone.
  • the invention is based on a more thorough transformation of the stator cross section in accordance with the requirements made within the different sectors of the compressor, the stator cross section being substantially composed of three arcs or curves of substantially circular shape.
  • One of these curves has the same radius as the rotor and forms a transition zone between the high pressure and low pressure side, as in the embodiment with countersunk rotor type.
  • the two other curves have respectively a somewhat greater and somewhat smaller radius of curvature than the mean radius of curvature of the stator, the greater radius of curvature being imparted to the inlet side and the smaller one to the outlet side.
  • the stator housing thus acquires a cross-section acoording to the accompanying claims, resulting in reduced power losses both at the inlet and outlet as well as of waste space, while at the same time securing smooth movements of the vanes along the stator surface.
  • FIG. 1 shows a conventional rotary compressor with a stator having circular cross-section.
  • FIG. 2 shows an indicator diagram for such a compressor.
  • FIG. 3 shows a rotary compressor according to the invention in which the stator defines a single operating cycle of 360.
  • FIG. 4 is similar to FIG. 3, and shows a comparison with the compressor with countersunk rotor.
  • FIGS. 5 and 6 show compressors according to the invention designed with double chambers defining two operating cycles of 360 each, the first with and the second without discharge valves.
  • FIG. 7 shows an indicator diagram for the latter embodiment.
  • FIG. 1 shows a rotary compressor of the sliding vane type comprising a single chamber having a pressure valve 1, a rotor 2 and a stator 3 and vanes 4.
  • the vertical diameter in the compressor is the dividing line between the inlet portion and the outlet portion.
  • the inlet op ening is designated by ref. numeral 7.
  • the dead space is shown in solid and consists of an outlet 6 and the space 5 between the rotor 2, the stator 3 and the vane 4 in the position where the vane 4 is about to pass across the entrance of the outlet 6.
  • FIG. 2 shows a schematical indicator diagram which applies to the working cycle ofa vane, in which 8 designates useful compressor work, 9 loss due to dead space, 10 loss due to throttlings in gaps and valve system at the outlet side and 11 loss due to throttling effects at the inlet side.
  • the volumetric loss 11 may be reduced by increasing the flow areas on the inlet side.
  • FIG. 3 characterised by its unsymmetrical shape which provides an increased inlet area 12, and an increased gap area 13 while simultaneously reducing the waste space 5.
  • This profile also provides a more efficient sealing in the area 14 between the highand the low pressure sides where the statorand the rotor radii are the same, but it should not be confused with the conventional so called countersunk rotor", the only object of which is to provide an improved sealing in this same area.
  • FIG. 4 in which 15 is a countersunk rotor profile and 16 is the profile according to the invention, the respective sealing gaps of the two profiles being indicated by ref. numerals l7 and 14. It is important to note that the wedge shaped space 5 after the outlet holes 6 is reduced or fully eliminated, which implies that the work which would otherwise have been required for draining the working medium from this volume is regained.
  • FIG. 5 shows the present invention adapted to a rotary compressor of the sliding vane type in a double-chamber embodiment, and of course the adaptation can be made to an optional number of working chambers.
  • FIG. 6 shows the unsymmetrical stator profile adapted to a rotary compressor without pressure valves and FIG. 7 a schematic indicator diagram for this embodiment.
  • a rotary compressor of the sliding vane type comprising:
  • a cylindrical rotor housed within said stator and defining therebetween a low pressure portion yaving an inlet for the working fluid and a high pressure portion having an outlet for the working fluid;
  • one of said arcs having the same radius as said rotor and forming a transition zone providing a sliding seal between the stator and the rotor in said zone;
  • a third arc extending from said second arc having a radius of curvature smaller than the mean radius of the stator defining together with the rotor 21 high pressure zone decreasing progressively in volume to merge with the other end of said transition zone.

Abstract

A rotary compressor of the sliding vane type, in which the vanes of the rotor slide resiliently along the inner surface of the stator the cross section profile of which defines three separate substantially circular arcs one of which has the same radius as the rotor and forms a transition zone or sealing area between the high pressure side and the low pressure side, the profile defining the inlet side or low pressure side having a radius of curvature which is greater than the mean radius of the stator and the profile defining the outlet side or high pressure side having a radius smaller than the mean radius of the stator, whereby the space between the inner surface of the stator increases continuously from substantially zero at the inlet side of the transition zone to its predetermined optimum and thereafter decreases continuously back to substantially zero at outlet side of the transition zone.

Description

United States Patent [191 Glanvall Nov. 4, 1975 ROTARY COMPRESSOR OF THE SLIDING [73] Assignee: Stal Refrigeration AB, Norrkoping,
Sweden [22] Filed: Aug. 9, 1973 [21] Appl. No.: 386,953
[30] Foreign Application Priority Data FOREIGN PATENTS OR APPLICATIONS 1,091,637 9/1952 France 418/266 888,477 ll/1942 France ..4l8/264 Primary ExaminerC. J. Husar Assistant ExaminerO. T. Sessions Attorney, Agent, or FirmEn'c Y. Munson [57] ABSTRACT A rotary compressor of the sliding vane type, in which the vanes of the rotor slide resiliently along the inner surface of the stator the cross section profile of which defines three separate substantially circular arcs one of which has the same radius as the rotor and forms a transition zone or sealing area between the high pressure side and the low pressure side, the profile defining the inlet side or low pressure side having a radius of curvature which is greater than the mean radius of the stator and the profile defining the outlet side or high pressure side having a radius smaller than the mean radius of the stator, whereby the space between the inner surface of the stator increases continuously from substantially zero at the inlet side of the transition zone to its predetermined optimum and thereafter decreases continuously back to substantially zero at outlet side of the transition zone.
2 Claims, 7 Drawing Figures US. Patent Nov. 4, 1975 Sheet 1 of 2 3,917,438
US. Patent Nov. 4, 1975 Sheet 2 of2 3,917,438
ROTARY COMPRESSOR OF THE SLIDING VANE TYPE 1 BACKGROUND OF THE INVENTION leakage. between the high pressure and low pressure 1 sides and, in the case of compressors having discharge valves, re-expansion of the compressed medium confined in thearea between the high pressure side and the lower pressure side.
Various attempts have been made to minimizethese losses, among others by providing a so-called countersunk rotor, which means that a recess has been made in the wall of the otherwise circular rotor housing, which recess has the same radius as the rotor which will then slide closely the stator housing surface along a certain portion thereof. This arrangement will considerably reduce leakage between the high pressure and low pressure side, but at the same time, it will cause an uneven movement of the vanes which, along the rear edge of said recess, may give rise to ajumping or ricocheting of the vanes on the stator surface.
SUMMARY OF THE INVENTION The invention is based on a more thorough transformation of the stator cross section in accordance with the requirements made within the different sectors of the compressor, the stator cross section being substantially composed of three arcs or curves of substantially circular shape. One of these curves has the same radius as the rotor and forms a transition zone between the high pressure and low pressure side, as in the embodiment with countersunk rotor type. The two other curves have respectively a somewhat greater and somewhat smaller radius of curvature than the mean radius of curvature of the stator, the greater radius of curvature being imparted to the inlet side and the smaller one to the outlet side.
The stator housing thus acquires a cross-section acoording to the accompanying claims, resulting in reduced power losses both at the inlet and outlet as well as of waste space, while at the same time securing smooth movements of the vanes along the stator surface.
BRIEF DESCRIPTION OF THE DRAWING FIG. 1 shows a conventional rotary compressor with a stator having circular cross-section.
FIG. 2 shows an indicator diagram for such a compressor.
FIG. 3 shows a rotary compressor according to the invention in which the stator defines a single operating cycle of 360.
FIG. 4 is similar to FIG. 3, and shows a comparison with the compressor with countersunk rotor.
FIGS. 5 and 6 show compressors according to the invention designed with double chambers defining two operating cycles of 360 each, the first with and the second without discharge valves.
FIG. 7 shows an indicator diagram for the latter embodiment.
DESCRIPTION OF A PREFERRED INVENTION FIG. 1 shows a rotary compressor of the sliding vane type comprising a single chamber having a pressure valve 1, a rotor 2 and a stator 3 and vanes 4. The vertical diameter in the compressor is the dividing line between the inlet portion and the outlet portion. The inlet op ening is designated by ref. numeral 7. The dead spaceis shown in solid and consists of an outlet 6 and the space 5 between the rotor 2, the stator 3 and the vane 4 in the position where the vane 4 is about to pass across the entrance of the outlet 6.
FIG. 2 shows a schematical indicator diagram which applies to the working cycle ofa vane, in which 8 designates useful compressor work, 9 loss due to dead space, 10 loss due to throttlings in gaps and valve system at the outlet side and 11 loss due to throttling effects at the inlet side. The power loss 9 may be reduced by reducing the dimensions of 5 or 6 or both by reducing the outlet area 6 and/or relocating the position of the outlet opening 6 to a =360. However, such modifications result in reduced flow areas and thus an increased pressure drop over gap and outlet opening areas, and consequently the power loss 10 would increase. The volumetric loss 11 may be reduced by increasing the flow areas on the inlet side.
In order to minimize these efficiency-reducing factors, a new stator profile has been designed as shown in FIG. 3 characterised by its unsymmetrical shape which provides an increased inlet area 12, and an increased gap area 13 while simultaneously reducing the waste space 5. This profile also provides a more efficient sealing in the area 14 between the highand the low pressure sides where the statorand the rotor radii are the same, but it should not be confused with the conventional so called countersunk rotor", the only object of which is to provide an improved sealing in this same area. The difference will be clear from FIG. 4 in which 15 is a countersunk rotor profile and 16 is the profile according to the invention, the respective sealing gaps of the two profiles being indicated by ref. numerals l7 and 14. It is important to note that the wedge shaped space 5 after the outlet holes 6 is reduced or fully eliminated, which implies that the work which would otherwise have been required for draining the working medium from this volume is regained.
Another considerable advantage resulting from the new profile is the fact that, the profile extends tangentially beyond the gap 14, as opposed to the countersunk rotor profile which, beyond the sealing gap 17, changes abruptly into a new profile shape, causing a rapid change of movement of the vane which may jeopardize proper vane function with constant contact between the vane tips and the stator surface. FIG. 5 shows the present invention adapted to a rotary compressor of the sliding vane type in a double-chamber embodiment, and of course the adaptation can be made to an optional number of working chambers.
FIG. 6 shows the unsymmetrical stator profile adapted to a rotary compressor without pressure valves and FIG. 7 a schematic indicator diagram for this embodiment.
It should be noted that all of the figures have been drawn to somewhat exaggerated proportions in order to give as clear a picture as possible.
I claim:
I. A rotary compressor of the sliding vane type comprising:
a. a stator;
b. a cylindrical rotor housed within said stator and defining therebetween a low pressure portion yaving an inlet for the working fluid and a high pressure portion having an outlet for the working fluid;
c. a plurality of vanes extending from the exterior surface of said rotor in resilient slidable engagement with the inner surface of said stator;
d. the cross sectional profile of said stator defining three separate, substantially circular arcs;
e. one of said arcs having the same radius as said rotor and forming a transition zone providing a sliding seal between the stator and the rotor in said zone;
f. a second arc extending from one end of said transition zone having a radius of curvature greater than the mean radius of the stator and defining together with said rotor a low pressure zone increasing progressively in volume from said transition zone to a predetermined optimum; and
. a third arc extending from said second arc having a radius of curvature smaller than the mean radius of the stator defining together with the rotor 21 high pressure zone decreasing progressively in volume to merge with the other end of said transition zone.

Claims (2)

1. A rotary compressor of the sliding vane type comprising: a. a stator; b. a cylindrical rotor housed within said stator and defining therebetween a low pressure portion having an inlet for the working fluid and a high pressure portion having an outlet for the working fluid; c. a plurality of vanes extending from the exterior surface of said rotor in resilient slidable engagement with the inner surface of said stator; d. the cross sectional profile of said stator defining three separate, substantially circular arcs; e. one of said arcs having the same radius as said rotor and forming a transition zone providing a sliding seal between the stator and the rotor in said zone; f. a second arc extending from one end of said transition zone having a radius of curvature greater than the mean radius of the stator and defining together with said rotor a low pressure zone increasing progressively in volume from said transition zone to a predetermined optimum; and g. a third arc extending from said second arc having a radius of curvature smaller than the mean radius of the stator defining together with the rotor a high pressure zone decreasing progressively in volume to merge with the other end of said transition zone.
2. A rotary compressor according to claim 1, in which the tangential plane of said third arc at the point of merger with said transition zone crosses the rotor and in which the transition zone and said second arc have a common tangential plane at their point of merger.
US386953A 1972-08-24 1973-08-09 Rotary compressor of the sliding vane type Expired - Lifetime US3917438A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4410305A (en) * 1981-06-08 1983-10-18 Rovac Corporation Vane type compressor having elliptical stator with doubly-offset rotor
US4415322A (en) * 1978-02-10 1983-11-15 Idram Engineering Company Est. Rotary machine with controlled retractable elements
US4501537A (en) * 1981-10-23 1985-02-26 Diesel Kiki Co., Ltd. Vane compressor having an endless camming surface minimizing torque fluctuations
US4898526A (en) * 1986-08-12 1990-02-06 Eagle Industry Co., Ltd. Vane pump with axial inlet and peripheral tangential outlet
DE19924645A1 (en) * 1999-05-28 2000-11-30 Lmf Leobersdorfer Maschinenfab Rotary vane compressor or vacuum pump
WO2007140758A1 (en) * 2006-06-07 2007-12-13 Ixetic Hückeswagen Gmbh Vane pump
CN103982430A (en) * 2014-04-09 2014-08-13 浙江飞越机电有限公司 High-pumping speed rotary-vane vacuum pump chamber structure and design method for pump chamber profile
CN113250957A (en) * 2021-04-19 2021-08-13 湖南腾智机电有限责任公司 Single-rotor vacuum pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4107848A (en) * 1977-02-07 1978-08-22 Pmc Industries, Inc. Profiler

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1123240A (en) * 1913-08-16 1915-01-05 George H Bubel Engine-starting device.
US3044687A (en) * 1959-02-17 1962-07-17 Paul H Davey Wear-resistant vane for rotary compressor
US3121421A (en) * 1962-04-11 1964-02-18 Taft M Peterson Rotary internal combustion engine
US3774397A (en) * 1971-08-04 1973-11-27 Energy Res Corp Heat engine
US3820924A (en) * 1972-12-15 1974-06-28 Chrysler Corp Rotary vane refrigerant gas compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1123240A (en) * 1913-08-16 1915-01-05 George H Bubel Engine-starting device.
US3044687A (en) * 1959-02-17 1962-07-17 Paul H Davey Wear-resistant vane for rotary compressor
US3121421A (en) * 1962-04-11 1964-02-18 Taft M Peterson Rotary internal combustion engine
US3774397A (en) * 1971-08-04 1973-11-27 Energy Res Corp Heat engine
US3820924A (en) * 1972-12-15 1974-06-28 Chrysler Corp Rotary vane refrigerant gas compressor

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4415322A (en) * 1978-02-10 1983-11-15 Idram Engineering Company Est. Rotary machine with controlled retractable elements
US4410305A (en) * 1981-06-08 1983-10-18 Rovac Corporation Vane type compressor having elliptical stator with doubly-offset rotor
US4501537A (en) * 1981-10-23 1985-02-26 Diesel Kiki Co., Ltd. Vane compressor having an endless camming surface minimizing torque fluctuations
US4898526A (en) * 1986-08-12 1990-02-06 Eagle Industry Co., Ltd. Vane pump with axial inlet and peripheral tangential outlet
DE19924645A1 (en) * 1999-05-28 2000-11-30 Lmf Leobersdorfer Maschinenfab Rotary vane compressor or vacuum pump
WO2007140758A1 (en) * 2006-06-07 2007-12-13 Ixetic Hückeswagen Gmbh Vane pump
CN103982430A (en) * 2014-04-09 2014-08-13 浙江飞越机电有限公司 High-pumping speed rotary-vane vacuum pump chamber structure and design method for pump chamber profile
CN103982430B (en) * 2014-04-09 2016-02-17 浙江飞越机电有限公司 The design method of high pumping rate rotary-vane vaccum pump pump chamber structure and pump chamber profile
CN113250957A (en) * 2021-04-19 2021-08-13 湖南腾智机电有限责任公司 Single-rotor vacuum pump

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GB1428279A (en) 1976-03-17
DE2340794A1 (en) 1974-03-07
JPS52253B2 (en) 1977-01-06
JPS4959303A (en) 1974-06-08

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