EP0240823A2 - Compresseur à piston roulant - Google Patents

Compresseur à piston roulant Download PDF

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Publication number
EP0240823A2
EP0240823A2 EP87104228A EP87104228A EP0240823A2 EP 0240823 A2 EP0240823 A2 EP 0240823A2 EP 87104228 A EP87104228 A EP 87104228A EP 87104228 A EP87104228 A EP 87104228A EP 0240823 A2 EP0240823 A2 EP 0240823A2
Authority
EP
European Patent Office
Prior art keywords
rotary
piston compressor
compressor according
rotary piston
sleeve
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.)
Granted
Application number
EP87104228A
Other languages
German (de)
English (en)
Other versions
EP0240823A3 (en
EP0240823B1 (fr
Inventor
Hans-Peter Dipl.-Ing. Schabert
Max Dipl.-Ing. Heller
Klaus Dipl.-Ing. Zach (Fh)
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0240823A2 publication Critical patent/EP0240823A2/fr
Publication of EP0240823A3 publication Critical patent/EP0240823A3/de
Application granted granted Critical
Publication of EP0240823B1 publication Critical patent/EP0240823B1/fr
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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y10T137/86421—Variable

Definitions

  • the invention relates to a rotary piston compressor with a piston rotating in a cylinder, which is carried by a shaft rotating in the same direction, and with inlet and outlet openings in the cylinder, which are provided with control elements.
  • control members are designed in particular as spring-loaded flaps or valves which open or block the passage cross section with a practically straight-line movement. Because of their reciprocating movement, such control elements are not suitable for fast switchovers, which are required at high speeds. It is therefore the object of the invention to improve rotary piston compressors of the type mentioned above in such a way that they are also suitable for high speeds. This is particularly important for mechanically driven rotary piston compressors which are rigidly coupled to an internal combustion engine and are used to charge the internal combustion engine.
  • a rotary slide valve is arranged as a control element outside the cylinder in a sleeve provided with slots and is connected to the shaft in a continuous, synchronized rotary movement and that the relative position of the rotary slide valve and sleeve is adjustable relative to one another.
  • rotary valve a roller-shaped body is meant, so that passages provided on its periphery alternately communicate with the slots in the sleeve, which can also be an integral part of the compressor housing. The adjustment of the relative position, which serves to change the passage cross sections, takes place primarily in the axial direction.
  • a rotary valve arranged on the pressure side can be controlled in the invention in such a way that it opens as soon as the pressure in the cylinder has risen to the back pressure of the pressure line.
  • the corresponding angle of rotation of the piston is e.g. about 160 ° in the case of a rotary piston compressor that compresses from 1000 hPa to 2000 hPa.
  • a rotary valve can also be used on the suction side of the rotary piston compressor. There it allows for a continuous control of the amount of gas drawn in at a fixed speed. For example, the rotary valve at open a crank angle between 0 and 25 ° of the shaft supporting the cylinder and close at a crank angle of at most 360 °. This results in the maximum delivery rate of the compressor for the closing angle of 360 °, ie the rotary valve remains practically constantly open. At smaller closing angles, which result in a shorter filling time, the amount of gas drawn in decreases, as is also the case when the throttle valve is gradually closed in a motor vehicle. Compared to the highly lossy throttle control, the design according to the invention as a periodically intermittent fill quantity control, however, delivers a significantly better efficiency.
  • the coupling to the compressor shaft which is desired for a constant synchronized rotary movement of the rotary slide valve can advantageously take place in such a way that the rotary slide valve and the shaft are connected to one another by a toothing.
  • Gears, toothed chains or toothed belts are primarily suitable as toothed links. It can be obtained with non-circular gears periodically non-uniform rotary slide movements, which allow quick closing after a long time with a large passage cross-section. This minimizes the small throttling losses that still occur when regulating the fill quantity.
  • the rotary valve for changing the passage cross-section relative to the sleeve is not only adjustable in the axial direction, but is also rotatable by a smaller angle than ⁇ 90 °, for example by 80 °, because one so that the temporal change in the opening cross-section can better capture the current suction volume flow during rotation.
  • the sleeve is actuated on the end face opposite the rotary valve drive, because it does not reach the area of the actuators of the rotary valve.
  • a possibility will also be presented later of having the adjustment act on the rotary slide valve and providing it on one side in a space-saving manner together with its drive.
  • the return spring e.g. the suction quantity of the rotary piston compressor is regulated to a minimum value suitable for an internal combustion engine as idling.
  • a coupling with the accelerator pedal and an idle adjustment screw can be provided.
  • the sleeve preferably being made of plastic and surrounding a rotary valve made of metal. It is particularly advantageous to install the plastic sleeve with play in the housing so that it can expand locally when a temperature peak occurs at a friction point.
  • the rotary valve can also be designed so that it has opposite openings and is flowed through diametrically.
  • the speed of the rotary valve must be half or a third of the shaft speed.
  • the invention can be implemented in such a way that a common rotary slide valve for both Piston parts are provided, the passage openings are offset in the axial circumferential direction.
  • the offset can be 90 °, for example.
  • control option by means of the rotary valve should remain available even when the internal combustion engine is cold started.
  • the internal combustion engine is still cold, not only should the cooling of the intake air occurring at part load be compensated, but additional heat should be added to it if possible.
  • This task can be solved by a switchable internal throttle bypass.
  • FIG. 3 shows a section along the rotary slide axis drive and adjustment of a rotary slide from the same side.
  • FIGS. 7 and 8 developments of the rotary valve show passage cross sections and their changes by adjusting the rotary valve and sleeve.
  • the rotary piston compressor shown in FIGS. 1 and 2 is designed in tandem, because in its housing 1, which is made of light metal casting, the shaft 2 carries two piston parts 3 and 4 offset by 180 ° a rolling piston 5.
  • the two piston parts 3 and 4 in the same design comprise cylindrical tube pieces 6 made of stainless steel with a wall thickness of, for example, 1.2 mm and a diameter of 145 mm.
  • the pipe sections 6 are held with a thin-walled shell 7 on a hub body 8 which is fastened with a ball bearing 10 on a cranked section 9 of the shaft 2, so that the piston part 3 is pressed elastically against the wall 11 of the cylinder 1.
  • the suction line of the compressor is 500 m3 / h.
  • the shaft 2 carries, outside the housing 1, a pulley 12 for a V-belt, with which the connection to an internal combustion engine, not shown, is established.
  • the toothed belt 16 establishes the connection to a rotary valve 20 which is arranged in an inlet opening 17 and is mounted in the housing 1 as a regulating member on the suction side.
  • the rotary valve 20 projects into a pipe socket 21 formed by the housing 1 with a ball bearing 22 which carries a toothed belt pulley 23.
  • a toothed belt pulley 23 On the toothed belt pulley 23, the flange 25 of a hollow shaft 26 is fastened in a flexible manner, which projects into the pipe socket 21. There it engages with a head piece 28 at its free end, which is provided with curved teeth 29, in grooves 30 of a further hollow shaft 31, which forms the main piece of the rotary valve 20.
  • the hollow shaft 31 is made of metal, for example stainless steel. It is on the end of the housing 1 facing away from the toothed belt pulley and the V-belt pulley 12 with an inwardly projecting Provide flange 34 on which a push rod 35 engages with a ball bearing 50. With the rod 35, an axial displacement of the hollow shaft 31 relative to a sleeve 36 made of plastic can be achieved, which tightly surrounds the hollow shaft 31 of the rotary valve 20. Since both in the sleeve 36 and in the hollow shaft 31 at least partially oblique slots 37, 38 are provided, for example triangular or trapezoidal, a different passage cross section can be set depending on the angular position of the rotary valve 20 by the axial displacement of the hollow shaft 31. In this way, the suction quantity and thus the delivery rate of the rotary piston compressor can be varied within wide limits.
  • the rotary piston compressor designed in tandem has a central partition 40 between the two piston parts 3 and 4.
  • a valve 42 is arranged in the housing 1, which can be actuated by a magnet 43.
  • An internal throttle bypass is connected with the valve 42 between the two cylinder parts, which are connected to one another by a longitudinal bore 46 and transverse bores 47 and 48. With this bypass, the cold start of an internal combustion engine with a rotary piston compressor can be facilitated. As long as the bypass is kept open, there is a back and forth lossy air flow, which causes the intake air to heat up.
  • the bypass can also be arranged in such a way that it connects regions on the circumference of the cylinder 1 that are at a distance from one another.
  • FIG. 3 shows another type of actuation of the rotary valve 20 in a section along the axis of the rotary valve 20.
  • the drive and adjustment act on the same side of the rotary valve.
  • a pipe section 62 is mounted on the housing 1 of the rotary piston compressor with two ball bearings 60 and 61 spaced apart from one another, which is expanded to a gear 63 on its side facing the housing 1.
  • the other end of the pipe section 62 is formed into a flange 65.
  • a counter flange is fastened with screws 66, which is designed to be flexible with respect to the axial direction by means of incisions 68 and 69.
  • the flange 67 carries a hollow shaft piece 70 pointing towards the housing 1, into which a counterpart 72 with an arch toothing 73 located at the end is inserted.
  • the curved toothing 73 in turn engages in the grooves 30 of the hollow shaft 31 of the rotary valve 20.
  • a rod 80 projects through the flange 67 and is fixed in the hollow shaft 31 with a ball bearing 81.
  • the rod 80 is used to adjust the rotary valve 20 in the longitudinal direction.
  • it is provided with a spherical actuation button 83 at the end remote from the rotary valve 20.
  • the drive of the rotary slide valve 20 and its axial adjustment device are provided at the same end and are structurally combined in a very small space.
  • two elliptical gears 85 and 86 are used to generate the non-uniform but periodic movement, which mesh with each other.
  • the gear 85 sits eccentrically, namely with its one focal point, on the hollow shaft 31 of the rotary valve 20, the gear 86 also eccentrically on an intermediate shaft 87.
  • the intermediate shaft 87 is connected to a countershaft gear 88 which meshes with a smaller countershaft gear 89.
  • the gear 89 sits on the shaft 2 of the rotary piston compressor.
  • the speed of rotation can be varied in a ratio of up to 1: 2.
  • the oval gear 85 like the oval gear 86, is not mounted in the focal point of an ellipse determining the gear circumference, but rather in the center of the gear.
  • the maximum speed of the rotary valve 20 relates to the minimum speed like the inverse ratio of the gear radii.
  • FIG. 6 shows that a periodically non-uniform movement of the rotary valve 20 can also be achieved with a coupling square.
  • the coupling quadrangle comprises a crank 90 which is connected to the hollow shaft 31 of the rotary valve 20.
  • the crank 90 is connected by a connecting rod 91 to a second crank 92, which sits on an intermediate shaft 93 carrying the gear 88.
  • the gear 88 meshes with the counter gear 89.
  • this gear enables ratios of the minimum to the maximum rotary valve speed of approximately 1: 3.5.
  • Figure 7 shows a development of the sleeve 36 and the rotary valve 20 with e.g. 40 mm diameter in the event that the rotary valve 20 is driven at half the speed of the shaft 2.
  • Sleeve 36 and rotary valve 20 are traversed by the gas flow on the suction side. They each have two slots 37 with an offset of 180 ° on the circumference, namely the two triangular slots 37, 37a in the rotary slide valve 20 and the slots 38 and 34 in the sleeve 36.
  • the slot 38 of the sleeve 36 connected to the cylinder 1 has a similar one Triangular shape like the slots 37, 37a of the rotary valve 20. However, the triangle 38 is turned upside down.
  • the slot 39 of the sleeve 36 connected to the suction line 17, on the other hand, is rectangular.
  • the slots 37, 37a When moving the rotary valve 20 to the left by the stroke 98 of e.g. 40 mm, the slots 37, 37a come into positions 37 ', 37a'. They then overlap with the slits 38, 39 to a much greater extent, since the flow cross-sections 101, 102 with dashed lines are created. They also remain open over a large range of rotation angles.
  • the axial displacement 98 of the rotary valve 20 thus causes a strong increase in the suction power of the compressor and leads to an increase in the boost pressure in the connecting pipeline 53 to the internal combustion engine.
  • the opening area reaches its maximum value somewhat later than the theoretically approximately sinusoidal course of the volume flow in the rotary piston compressor during suction.
  • the inertia of the real air column is taken into account in the sense that the throttling losses in the free slot cross section, ie in the overlap of the passages 38 and 37, are minimized.
  • the start of the opening in time (at 0 °, for example) is independent of the axial position of the rotary valve 20.
  • a displacement in the circumferential direction between the rotary valve 20 and its toothed belt pulley 23 must therefore be superimposed on the displacement stroke 98 (40 mm) (for example by ⁇ 85 °), so that the overall adjustment runs in the direction of arrow 96.
  • the teeth of the curved tooth intermediate piece 29 are rotated towards the rotary slide 20 by 45 ° to the axis.
  • the filling quantity is controlled by pushing or pulling on the opposite end (with 45 ° setting the risk of self-locking due to tooth friction is the lowest).
  • the shape of the triangular or trapezoidal slot 37 is chosen so that the long slope coincides with the displacement device of the rotary valve 20.
  • the opposite side is either axially parallel, but can also deviate from it.
  • the slots 37 cover approximately 64% (2 ⁇ 32%), the webs the residual angle 36% (2 ⁇ 18%) of the hollow shaft 31 of the rotary valve.
  • the slots 37 are shortened by, for example, 20% of the original triangular width in order to be able to arrange slots 37 which are as wide as possible on the circumference of the rotary valve 20.
  • the reduction does indeed reduce the rate of change in area that can be achieved at almost full opening just before the flow is shut off; however, since the flow has already decreased considerably on its own (sine line), the throttling loss that arises as a result is modest.
  • the axial stroke of the rotary valve 20 can be e.g. 15% longer than the length of the original triangular slot. This creates a particularly large passage cross-section and low throttle losses at full load.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP87104228A 1986-04-04 1987-03-23 Compresseur à piston roulant Expired - Lifetime EP0240823B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3611326 1986-04-04
DE19863611326 DE3611326A1 (de) 1986-04-04 1986-04-04 Rollkolbenverdichter

Publications (3)

Publication Number Publication Date
EP0240823A2 true EP0240823A2 (fr) 1987-10-14
EP0240823A3 EP0240823A3 (en) 1988-09-28
EP0240823B1 EP0240823B1 (fr) 1991-11-21

Family

ID=6297935

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87104228A Expired - Lifetime EP0240823B1 (fr) 1986-04-04 1987-03-23 Compresseur à piston roulant

Country Status (5)

Country Link
US (1) US4793779A (fr)
EP (1) EP0240823B1 (fr)
JP (1) JPS62240494A (fr)
BR (1) BR8701547A (fr)
DE (2) DE3611326A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH684020A5 (de) * 1990-04-18 1994-06-30 Bauer Kompressoren Trockenlaufender Hubkolben-Kompressor.
JPH05256251A (ja) * 1992-03-12 1993-10-05 Aisin Seiki Co Ltd 可変容量圧縮機
CN1329664C (zh) * 2002-12-25 2007-08-01 乐金电子(天津)电器有限公司 旋转式压缩机的吸气结构
US7819131B2 (en) * 2005-02-14 2010-10-26 Cameron International Corporation Springless compressor valve
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0175639A1 (fr) * 1984-09-11 1986-03-26 ATP Arbeitsgruppe Technische Photosynthese GmbH & Co. Produktions KG Machine thermodynamique
EP0212570A2 (fr) * 1985-08-26 1987-03-04 Siemens Aktiengesellschaft Compresseur à piston roulant

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1990263A (en) * 1932-05-23 1935-02-05 Hydraulic Press Mfg Co Pump
US2063503A (en) * 1933-12-08 1936-12-08 S H G Inc Fluid pump
US3224462A (en) * 1963-09-12 1965-12-21 Edwin B Lopker Non-metal valve
US3208388A (en) * 1964-06-03 1965-09-28 Clarence O Glasgow Pump
US3535059A (en) * 1968-07-02 1970-10-20 Atomic Energy Commission Rotary engine valve
US3650295A (en) * 1970-04-20 1972-03-21 Richard J Smith Rotary valve
US3867075A (en) * 1974-07-22 1975-02-18 Horst Power Systems Inc Rotary engine with rotatable thrust heads in a toroidal chamber
US4245968A (en) * 1979-12-06 1981-01-20 Veda, Inc. Lubricating system for pump and control valve therefor
DE3343908A1 (de) * 1983-12-05 1984-06-28 Kurt G. Ing.(grad.) 6710 Frankenthal Fickelscher Maschine, insbesondere arbeitsmaschine zum verdichten und foerdern von fluiden aller art

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0175639A1 (fr) * 1984-09-11 1986-03-26 ATP Arbeitsgruppe Technische Photosynthese GmbH & Co. Produktions KG Machine thermodynamique
EP0212570A2 (fr) * 1985-08-26 1987-03-04 Siemens Aktiengesellschaft Compresseur à piston roulant

Also Published As

Publication number Publication date
BR8701547A (pt) 1988-01-26
EP0240823A3 (en) 1988-09-28
EP0240823B1 (fr) 1991-11-21
US4793779A (en) 1988-12-27
DE3611326A1 (de) 1987-10-15
JPS62240494A (ja) 1987-10-21
DE3774604D1 (de) 1992-01-02

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