EP0283867B1 - Rollkolbenverdichter - Google Patents

Rollkolbenverdichter Download PDF

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Publication number
EP0283867B1
EP0283867B1 EP88103830A EP88103830A EP0283867B1 EP 0283867 B1 EP0283867 B1 EP 0283867B1 EP 88103830 A EP88103830 A EP 88103830A EP 88103830 A EP88103830 A EP 88103830A EP 0283867 B1 EP0283867 B1 EP 0283867B1
Authority
EP
European Patent Office
Prior art keywords
compressor according
piston
rotary piston
piston compressor
cylinder
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
EP88103830A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0283867A3 (en
EP0283867A2 (de
Inventor
Hans-Peter Dipl.-Ing. Schabert
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
Priority claimed from DE19873709493 external-priority patent/DE3709493A1/de
Application filed by Siemens AG filed Critical Siemens AG
Priority to AT88103830T priority Critical patent/ATE72302T1/de
Publication of EP0283867A2 publication Critical patent/EP0283867A2/de
Publication of EP0283867A3 publication Critical patent/EP0283867A3/de
Application granted granted Critical
Publication of EP0283867B1 publication Critical patent/EP0283867B1/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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • 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
    • F04C29/126—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 of the non-return type
    • F04C29/128—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 of the non-return type of the elastic type, e.g. reed 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
    • 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
    • F04C18/3442—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 the surfaces of the inner and outer member, forming the inlet and outlet opening
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the invention relates to a rotary piston compressor or, generally speaking, a rotary piston machine with a cylinder in or around which a thin-walled, radially resilient piston with a circular cross section is moved eccentrically by means of a rotationally symmetrical radial support from a drive shaft, the eccentricity being greater than half the difference in the diameters of cylinders and pistons.
  • the rotationally symmetrical support comprises a thin-walled shell made of permanently elastic material, which is attached at one end to a drive shaft and at the other end presses on the roller piston.
  • the shell acts as a spiral spring. Therefore, it is constantly deformed when the roller piston rotates.
  • the associated flexing work causes losses and leads to warming. This contradicts the isothermal compression desired per se. Therefore, the invention is based on the task of creating a rotationally symmetrical support that works with lower losses and yet is constructed just as simply as the known rotationally symmetrical support.
  • the support acts on the side of the piston remote from the cylinder, while locally there is play between the piston and the support at the point of contact of the piston with the cylinder.
  • the force necessary for the deformation of the rolling piston is not transmitted as a compressive force to the inside of the rolling piston, but rather from that of the sealing point, that is the point of contact between the rolling piston and the cylinder, which is remote from the cylinder, so to speak, is introduced as a tensile force.
  • the structure remains extremely simple.
  • the play between the rolling piston and the support at the aforementioned contact point is at least 0.1 mm. It is preferably 0.3 to 0.5 mm, namely during operation, i.e. primarily in the then prevailing temperature conditions. Furthermore, the diameter play of the undeformed piston compared to the support should be 0.2 to 0.5 times the play at the point of contact with the cylinder. With this play, the necessary space is created for the elastic deformation of the rolling piston, which results in the seal between the piston and the cylinder. On the other hand, the space is dimensioned as tightly as possible so that the support tightly encloses the flattened piston over a large part of its circumference (180 ° to 270 ° C) and secures it against vibrations.
  • the support according to the invention can engage on the end face of the piston from the inside or from the outside. A seal is then expediently arranged at the point of attack. With this gas losses are avoided, which would otherwise be caused by the game provided in the support according to the invention.
  • a preferred embodiment of the invention is that the piston is arranged within the cylinder and the support acts on a pressure band inserted in the piston with little play.
  • “Low backlash” means, for example, a value of 0.1 mm, based on the diameter, measured on the undeformed rotationally symmetrical components. A slight tension, as it could cause a negative game, would also be tolerable. Avoid strong tension, in which, as a result of constantly changing flattening, the two components lying one inside the other generate energy losses through mutual friction. Different temperatures and thermal expansion coefficients must also be taken into account, as well as the local tangential compressive stresses that slightly compress the circumference of the printing tape. Ultimately, it is important to achieve the desired "low backlash" characteristic for normal continuous operation.
  • the pressure band can also be firmly connected to the piston or form part of the piston. Otherwise, a sliding ring or a sliding layer between the pressure belt and the rolling piston can reduce friction losses.
  • the pressure band can also consist of a plurality of individual clamps which are suitably connected to the rolling piston, e.g. are riveted.
  • a clamp body connected to the drive shaft can enclose the pressure band on both sides.
  • the clamp body is preferably divided transversely to the piston axis so that a sufficient engagement between it and the pressure band can be achieved without difficult assembly.
  • Wear protection rings can be arranged on the sides of the printing tape.
  • the bracket support can contain roller bearings and cooling air holes. This also applies in the event that several clamp bodies are distributed over the axial length of the piston.
  • the last design is particularly advantageous if the axial length of the rolling piston is significantly larger than the diameter, e.g. B. from a length to diameter ratio of 3: 1.
  • the invention can also be implemented in such a way that the piston surrounds the cylinder.
  • the support comprises a tension band placed on the piston.
  • the tension band can once comprise the piston with little play and can be clamped with a ring connected to the drive shaft, preferably with an intermediate bearing of slide and wear protection rings.
  • you can the drawstring is designed to be flexible as a belt with a very large amount of play and to be provided with a tensioning roller outside the roller piston.
  • a pressure band each which has a step directed towards the center of the piston on one side, that a clamp roller that is open on one side towards the end faces of the piston engages over the step and that the clamp roller is firmly connected to the drive shaft.
  • the drive shaft with the clamp rollers provided at both ends results in a preassembled unit that can be used as a whole in the cylinder.
  • the drive shaft is fixed with the aid of the pressure bands arranged in the region of the ends of the piston, on the step of which toward the center of the piston the clamp rollers engage with axial play.
  • the axial guidance of the piston is taken over by the end faces of the cylinder.
  • the clamp roller can advantageously consist of a clamp bell and a deep groove ball bearing, which is connected to both the drive shaft and the clamp bell by a press fit.
  • the clamp bell can be a simple pressed sheet metal part and have an inner collar for contact with the deep groove ball bearing, so that an arrangement that is also fixed in the axial direction is produced.
  • the pressure band can also be fixed to the piston in the axial direction. This can be done in such a way that the pressure band is fixed with the aid of a sealing ring carrier assigned to the end faces of the cylinder, which is used to seal the piston on the end faces of the cylinder.
  • the pressure band can be blown into the sealing ring carrier on a collar, taking advantage of the different flexibility of the sealing ring carrier, which consists of plastic and / or the pressure band is made of metal, such as bronze.
  • the pressure tape can also rest on a step of the piston.
  • the sealing ring carrier can also protrude with an extension into an annular gap between the pressure band and the piston, so that the pressure band acts indirectly on the piston.
  • the sealing ring carrier acts as an intermediate layer and, with a suitable choice of material, can increase the sliding ability between the pressure band and piston, so that the running properties are improved and signs of abrasion are avoided.
  • the sealing ring carrier advantageously encloses a piston ring and a spring acting thereon in the axial direction. By enclosing it is meant that the piston ring and the spring are held in the sealing ring carrier and are designed as a preassembled unit.
  • the piston ring is conveniently slotted and made of plastic, coal or the like.
  • the design according to the invention leads to a very smooth-running rotary piston compressor.
  • This property can be further increased by cranking the drive shaft as a counterweight in a central area.
  • the shaft ends can be cranked in opposite directions, the length of the oblique shaft part being at most twice as large as the shaft diameter in the region of the staple roller, and between the oblique shaft part and the staple roller, a cylindrical wavelength of 70-100% of the width of the staple roller can be Deep groove ball bearings are available. This training can also be easily assembled for small piston diameters, as will be explained in more detail later.
  • the cranked shaft ends are advantageously in an outward extension of the cylinder end walls. This means that the overall volume of the rotary piston compressor is substantial to reduce.
  • the extension can have an inner collar for axially fixing the drive shaft.
  • the deep groove ball bearing can be fixed on the drive shaft with a locking ring, the nominal diameter of which is smaller than the inner diameter of the deep groove ball bearing but larger than the diameter of the cranked area of the shaft ends.
  • the advantage here is that the deep groove ball bearing can only be threaded over a short wavelength and nonetheless strength-reducing notch effects are avoided by a groove required for the locking ring.
  • Cooling air bores can be provided in the clamp bells and in the end faces of the cylinder. They allow intensive internal cooling so that an approximately isothermal compression can be achieved.
  • the invention can be advantageously carried out so that two counter-rotating pistons are arranged in parallel axes in two cylinder bores of a common housing in which a common slide for separating the suction and pressure chamber of the cylinder bores sits, and that the pistons over the clamp rollers can be carried by common lids on the front sides of the housing.
  • twin compressors considerable compressor outputs can be achieved in a small space.
  • This is particularly advantageous in such a way that a suction pipe and a pressure pipe are arranged parallel to the rolling pistons on opposite sides of the common housing. This gives a compressor with a flat shape that can be used even in limited spaces, e.g. in the engine compartment of a motor vehicle, can be accommodated well.
  • the rotary piston compressor according to FIG. 1 has a housing 1, which is composed of a cylindrical casing body 2 and the two flat side parts 3 and 4.
  • a drive shaft with roller bearings 7 is mounted in the side parts 3 and 4.
  • the drive shaft 6 has an eccentric 8, on which a clamp body 10 is fastened with a ball bearing 9 and has cooling air bores 11.
  • the clamp body 10 is part of the rotationally symmetrical support 12 of a cylindrical roller piston 13, which has a smaller diameter than the cylinder 1.
  • Half the difference in the diameter of the rolling piston 13 and cylinder 1 is smaller than the eccentricity of the eccentric 8 (for example by 4%, that is 10.0 mm instead of 10.4 mm), so that the rolling piston 13 on the side near the cylinder (in FIG 1, this is the top) by elastic deformation with a sealing force along a surface line against the cylinder wall.
  • the force required for the deformation is exerted by the clamp body 10 as a tensile force on the rolling piston 13, specifically on the underside of FIG. 1, via an annular region 15 which is firmly connected to the rolling piston 13.
  • This has a dovetail-shaped projection 16 which is symmetrical is.
  • the play "S" between the clamp body 10 and the projection 16, which has arisen as a result of the elastic flattening of the rolling piston 13, can be clearly seen.
  • the clamp body engages in the recesses 17 and 18 of the region 15 10 with a cross-sectionally U-shaped edge region 20, which is provided on both sides of the two-part clamp body 10.
  • the support 12 can exert a tensile force on the roller piston 13 on the side remote from the cylinder, while at the point of contact between roller piston 13 and cylinder 1 there is play S between the dovetail 16 and the edge region 20.
  • Its size S must be smaller than the clearance S1 between the edge region 20 and the rolling piston 13.
  • FIG. 3 shows that the dovetail-shaped structure of the piston 13 can also be achieved with individual clamps 24 which are riveted onto the piston 13 with rivets 25.
  • 36 clips 24 with a width of 12 mm can be attached to the inside of a roller piston 13, which has a diameter of 145 mm.
  • the rivets can e.g. Be 2 mm thick.
  • the support 12 of the rolling piston 13 acts on a pressure band 28 which has the T-profile shown in FIG. 4 in cross section.
  • the plastic ring 31 can be on the pressure ring 28 or on the inside of the Roll piston 13 be attached. It can be made, for example, in the form of a synthetic resin application.
  • the U-shaped edge 20 of the clamp body 10 encloses two plastic rings 33 and 34 which, as a wear protection layer, ensure that the metallic pressure band 28 can be guided without wear by the likewise metallic clamp body 10, in particular made of the same material.
  • the clamp body 10 is composed of two symmetrical ones Halves 35 and 36 assembled, which are connected by six screws 37 with thread M5.
  • an asymmetrical clamp body 10 with an edge 38 angled on one side engages over the end face of the rolling piston 13, which has a recess 39 there. Between this recess 39 and the edge 38 there is also a play S at the drawn point on the circumference, which represents a section through the point of contact of the rolling piston 13 with the cylindrical casing body 2.
  • the clamp body 10 grips directly and without play on the recess 39 of the rolling piston 13 and transmits the tensile force according to the invention. At the same time, it stabilizes the rolling piston 13 against deformations that could be generated by changing lateral gas forces, thereby preventing conceivable flutter phenomena at high speeds.
  • a seal carrier 40 is fastened, in which a sealing ring 41 with a spring 42 is accommodated.
  • the spring 42 is designed as a corrugated ring. It presses the sealing ring 41 in the axial direction against the clamp body 10, so that a seal is present despite the play between the edge 38 and the recess 39.
  • a rolling piston 54 is designed as an inclusion of a fixed cylinder 49.
  • the drive shaft 50 carries an eccentric 51 on which an eccentric bell 52 is attached.
  • the eccentric bell 52 engages a tension band 53, which in turn sits with little play on the outside of the rolling piston 54.
  • the rolling piston 54 is double-acting in this embodiment. This can best be seen from the cross section in FIG.
  • the rotating cylinder 49 contains two slides 57 and 58, which are under the action of a spring 60.
  • the slides separate an inner suction chamber 61 and 62 from an inner pressure chamber 63 and 64, which has a check valve 65 and 66, respectively.
  • the rolling piston 54 is driven in the exemplary embodiment according to FIG. 7 with flexible belts 69 and 70.
  • the belts both run around a drive roller 71 and a tension roller 72, with which the tensile stress exerted on the piston 54 can be predetermined.
  • the tensioning roller 72 also serves to stabilize the rolling piston 13 laterally.
  • the rolling piston 13 is also arranged on the outside of a rotating cylinder 49 equipped with two sliders 57 and 58.
  • the rolling piston 13 is pressed onto the cylinder 49 by two eccentrically mounted side disks 73 and 74. This creates the play-free contact of the rolling piston 13 on the side windows 73, 74 on the upper side of FIG. 8.
  • the play S is clearly visible, because there the cylinder 49 bulges the rolling piston 13 outward along its line of contact.
  • the side windows 73, 74 have seals 75, 76 towards the rolling piston 13, and seals 77, 78 towards the cylinder 49.
  • the rotary piston compressor is primarily intended for charging motor vehicle engines. It then conveys air with negative pressure. It can also be used as a vacuum pump or to pump other fluids.
  • the rotary piston compressor 100 according to FIG. 9 is intended for use in motor vehicles, in particular for charging four-stroke diesel engines. It comprises a cylindrical housing 102 with symmetrical cylinder covers 103 and 104 on the end faces. The housing 102 and the cover 104 are made of aluminum.
  • a roller piston 108 is seated in the cylinder 102. It is designed in the form of a cylindrical tube made of stainless steel and is held by a drive shaft 110 with the aid of a support 109.
  • the drive shaft 110 is a forgings. It is cranked in the middle region 111 and gives the piston 108 an eccentricity with respect to the axis of the cylinder 102 which is greater than the difference of half the diameter of the cylinder 102 and the piston 108. The excess results in ovalization at the contact point of the piston 108, which causes a contact pressure and accordingly good internal tightness.
  • the support 109 is provided in the end regions 114 and 115 of the piston 108. It is symmetrical and primarily comprises a clamp roller 117. This includes a deep groove ball bearing 118 and a clamp bell 119. The last is a pressed part made of sheet metal with a radial region 120, which is provided with holes 121 for the passage of cooling air, and two essentially axially oriented ring regions 124 and 125. The region 125 encloses the ball bearing 118 and holds it in the axial direction with a collar 126 pointing inwards. The area 124 extends over a pressure band 130 made of bronze, which forms a step 131 on its side facing the center of the cylinder, so that a ring area 132 with a reduced diameter is created.
  • the clamp bell 119 is fixed to the deep groove ball bearing and this to the drive shaft 110 by a press fit.
  • the ball bearing 118 is provided with sealing washers and filled with grease.
  • the pressure band 130 has an outer diameter in its central region which is the same size as the inner diameter of the piston 108. The part facing outwards is reduced in diameter, so that a ring piece 134 with a collar 135 is formed.
  • the seal ring carrier 138 has an annular groove 140 into which a piston ring 141 made of plastic or carbon is inserted.
  • the piston ring 141 is pressed under the action of a corrugated ring spring 142 against the end wall of the cylinder, namely against the cover 103.
  • the deep groove ball bearing 118 which sits with a press fit on a cylindrical region 145 of the drive shaft 110, is additionally held with a locking ring 146 which is embedded in a groove 147 in a region 148 with a reduced diameter. Following the retaining ring 146, the area 150 of the drive shaft 10 is again reduced in diameter.
  • the nominal diameter of the locking ring 146 is therefore 22 mm smaller than the inner diameter of the rolling bearing or the diameter of the cylindrical region 145, which is 25 mm, but larger than the outer diameter of an oblique shaft region 151, which belongs to the cranked shaft end 152.
  • the cranked shaft end 152 protrudes, as can be clearly seen in FIG. 10, into an outward extension 154 of the cover 103. There, a cylindrical region 155 is held with a ball bearing 156. The ball bearing 156 is fixed in the axial direction with an inwardly facing collar 157 of the extension 154. Therefore, the shaft 110 can be fastened with the piston 108 after the pushing in of the printing tape 130 only by pushing the covers 103 and 104 onto the drive shaft 110 from both sides. Cooling air bores 158 in the covers 103, 104 together with the holes ensure a cooling air flow through the piston 108 indicated by arrows.
  • the pressure band 130 ⁇ is not connected directly to the piston 108. In between, there is rather an extension 159 of the sealing ring carrier 138 ⁇ , which fills an intermediate space 160 which is substantially larger than the wall thickness of the ring region 124 of the clamp bell 119.
  • the pressure band 130band is axially fixed between a step 162 on the inside of the piston 108 and the sealing ring carrier 138 ⁇ , which in turn is axially fixed with its outer collar 139 between the piston 108 and the cylinder cover 103.
  • the rotary piston compressor according to the invention can advantageously be designed in the form of a twin compressor in which two cylinders are combined in a common housing 165.
  • the parallel recesses for the rolling pistons are closed on the end faces with cover plates 166, which have parallel extensions 154 for receiving the shaft ends.
  • the invention results in an extremely simple construction. It is therefore possible to achieve high revolutions and correspondingly high compressor outputs with a twin compressor, as shown in principle in FIG. At 4800 revolutions per minute and a volumetric efficiency of around 85%, a suction volume of 100 liters per second or 360 m3 per hour can be achieved.
  • the compressor is only about 300 mm long and about 120 mm high.
  • the cylinder diameter is 100 mm, while the piston diameter is 80 mm.
  • the pressure ratio can typically be 2.0.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP88103830A 1987-03-23 1988-03-10 Rollkolbenverdichter Expired - Lifetime EP0283867B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88103830T ATE72302T1 (de) 1987-03-23 1988-03-10 Rollkolbenverdichter.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3709493 1987-03-23
DE19873709493 DE3709493A1 (de) 1987-03-23 1987-03-23 Rollkolbenverdichter
DE3727697 1987-08-19
DE19873727697 DE3727697A1 (de) 1987-03-23 1987-08-19 Rollkolbenverdichter

Publications (3)

Publication Number Publication Date
EP0283867A2 EP0283867A2 (de) 1988-09-28
EP0283867A3 EP0283867A3 (en) 1990-02-28
EP0283867B1 true EP0283867B1 (de) 1992-01-29

Family

ID=25853810

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88103830A Expired - Lifetime EP0283867B1 (de) 1987-03-23 1988-03-10 Rollkolbenverdichter

Country Status (6)

Country Link
US (1) US4883414A (ko)
EP (1) EP0283867B1 (ko)
JP (1) JPS63253190A (ko)
KR (1) KR880011467A (ko)
AT (1) ATE72302T1 (ko)
DE (2) DE3727697A1 (ko)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007008225A2 (en) * 2004-08-14 2007-01-18 The State Of Oregon Acting By And Through The State Board Of Higher Education On Behalf Of Oregon State University Heat-activated heat-pump systems including integrated expander/compressor and regenerator
US7185625B1 (en) * 2005-08-26 2007-03-06 Shilai Guan Rotary piston power system
US20070231170A1 (en) * 2006-03-28 2007-10-04 Xiaogen Su Drive shaft for a compressor
DE102012003287A1 (de) * 2012-02-20 2013-08-22 Netzsch Pumpen & Systeme Gmbh Drehkolben
JP5743019B1 (ja) 2013-12-13 2015-07-01 ダイキン工業株式会社 圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1659107A (en) * 1922-06-19 1928-02-14 Rasmus M Hvid Rotary pump
US1543163A (en) * 1923-05-09 1925-06-23 Sven A Johnson Compressor
US1850394A (en) * 1928-03-05 1932-03-22 Horawa Frank Rotary compressor
DE877052C (de) * 1943-07-31 1953-05-18 Bosch Gmbh Robert Rollkolben fuer Verdichter, insbesondere Luftverdichter fuer Druckluftanlagen in Fahrzeugen
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
DE3530432A1 (de) * 1985-08-26 1987-02-26 Kraftwerk Union Ag Rollkolbenverdichter
DE3530436A1 (de) * 1985-08-26 1987-02-26 Kraftwerk Union Ag Rollkolbenverdichter

Also Published As

Publication number Publication date
KR880011467A (ko) 1988-10-28
EP0283867A3 (en) 1990-02-28
JPS63253190A (ja) 1988-10-20
EP0283867A2 (de) 1988-09-28
DE3727697A1 (de) 1989-03-02
ATE72302T1 (de) 1992-02-15
DE3868097D1 (de) 1992-03-12
US4883414A (en) 1989-11-28

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