EP0245427B1 - Screw rotor compressor and refrigeration plant - Google Patents
Screw rotor compressor and refrigeration plant Download PDFInfo
- Publication number
- EP0245427B1 EP0245427B1 EP19860906989 EP86906989A EP0245427B1 EP 0245427 B1 EP0245427 B1 EP 0245427B1 EP 19860906989 EP19860906989 EP 19860906989 EP 86906989 A EP86906989 A EP 86906989A EP 0245427 B1 EP0245427 B1 EP 0245427B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- port
- rotor
- outlet port
- groove
- 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
Links
Images
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
- 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
Definitions
- the present invention relates to a screw compressor, especially adapted for use within a refrigeration plant with two stage throttling.
- a compressor comprises a casing with a working space generally composed of intersecting bores with parallel axes enclosed by barrel and end walls and provided with spaced apart inlet and outlet ports for communication with inlet and outlet channels, respectively.
- Rotors each having helical lands and intervening grooves, are disposed in the bores and intermesh in pair.
- One rotor of the pair is of male rotor type formed such that at least the major portion of each land and groove is located outside the pitch circle of the rotor.
- the other rotor is of female rotor type formed such that at the major portion of each land and groove is located inside the pitch circle of the rotor.
- Two communicating groove portions thus form a chevron-shaped chamber having its base end disposed in a plane transverse to the axes of the bores and adjacent to the outlet port.
- the compressor is provided with capacity control means comprising a bleed port and a valve member having an axially displaceable control edge defining the actual size of the port.
- the compressor is further provided with means for additional supply of working fluid at a pressure higher than the normal inlet pressure.
- a compressor of the above type for use in a refrigeration plant is known from Swedish patent 382 663.
- This compressor is provided with an axially slidable valve of the type shown in Swedish patent 366 375, i.e. a valve member disposed in the barrel wall of the working space and including the intersection line between the bores so that the valve simultaneously adjusts a bleed port at one end and the outlet port at the other end.
- This valve member is provided with openings, for additional supply of gas from the first throttling stage, situated so that at maximum capacity the openings are disposed on such a distance from the inlet end wall that they communicate with a chevron-shaped chamber first after the initiation of the compression.
- a valve member of the type shown decreases for a certain displacement thereof the outlet volume, i.e. the volume of the chevron-shaped chamber when opening towards the outlet port, and the inlet volume, i.e. the volume of the chevron-shaped chamber when cut off from the bleed port, with the same quantity.
- the ratio between the inlet volume and the outlet volume, the built-in volume ratio thus increases with increasing bleed off. This effect is further accentuated when additional working fluid is supplied after the cut off from the bleed port.
- the bleed port In order to avoid too high built-in volume ratios and over-compression resulting therefrom the bleed port must when opened momentarily mean a considerable reduction of the inlet volume eventhough this on the other hand means a low built-in volume ratio resulting in under-compression.
- the possibility to vary the volumetric capacity of a compressor without too high losses in the adiabatic efficiency is thus limited.
- With additional supply openings in the valve member there is a further problem that those openings in order to maintain a higher pressure therein than the inlet pressure must be located on a considerable distance from the edge thereof controlling the bleed port. Consequently the bleed port in such a compressor must be situated closer to the inlet end wall than in normal compressors. In other words the reduction of the inlet volume when opening the bleed port can only be a fraction of that in earlier known compressors and consequently the range for variation of the volumetric capacity will be further reduced.
- the object of the present invention is to provide a compressor of the type specified where the range of capacity variation with high adiabatic efficiency is considerably extended simultaneously as the intermediate, additional supply pressure is on a steady high level required for an optimum process, which means that the over-all efficiency of the plant at part load is kept on a much higher level than that obtained by earlier used compressors.
- said capacity control means is situated peripherally out of the outlet port, that said additional supply means comprises a port within said capacity control valve located at an axial distance from said control edge at least corresponding to the axial distance between two consecutive lands of the facing rotor, and that separate means are provided for selective adjustment of the outlet port.
- a further improvement of the efficiency of the compressor may be obtained by providing the outlet port valve with injection means for a cooling and sealing liquid, said injection means being located such that it never communicates with any of the inlet and outlet ports or with the additional supply means, at least at low capacity reduction conditions.
- the compressor shown in Figs. 1 and 2 comprises a male rotor 10 provided with five helical lands 12 and intervening grooves 14-and a female rotor 16 intermeshing therewith and provided with six helical lands 18 each enclosing a rotor and intervening grooves 20.
- the rotors 10, 16 are mounted in a housing having low and high pressure end wall members and a barrel member 22 comprising two intersecting bores each enclosing a rotor.
- the housing is provided with an inlet port 24 at the low pressure end and extending as a relieved portion into the barrel wall and an outlet port 26 at the high pressure end.
- the barrel member 22 there are further two circular grooves intersecting with the barrel wall and each enclosing an axially adjustable valve member 28, 30 sealingly cooperating with the facing rotor 10, 16.
- One of the valve grooves forms the outlet port 26 and a pressure adjusting valve member 28 enclosed therein is provided with a control edge 32 defining the actual shape and size of the outlet port 26.
- the other valve groove is located in the wall of the bore enclosing the male rotor 10, peripherally out of the area of the outlet port 26 and encloses a capacity adjusting valve member 30 provided with a control edge 34 facing the inlet port 24 and at full capacity defining a part of the edge thereof, whereas at reduced capacity this edge defines the size and shape of a bleed port 36 communicating with the inlet port 24.
- the capacity valve 30 is further provided with an opening 38 for supply of additional working fluid at an intermediate pressure higher than that of the fluid supplied through the inlet port 24.
- This additional supply opening 38 is located at an axial distance from the control edge 34 corresponding to the axial distance between two consecutive lands 12 of the facing rotor 10.
- the pressure valve 28 is similarly provided with an opening 40 for supply of a cooling and sealing liquid, which in a refrigeration compressor may consist of liquefied working fluid preferably having a temperature below the condensing temperature, which will improve the efficiency of the compressor.
- a cooling and sealing liquid which in a refrigeration compressor may consist of liquefied working fluid preferably having a temperature below the condensing temperature, which will improve the efficiency of the compressor.
- a refrigeration plant which comprises a compressor 42 of the type specified above, a condenser 44 connected to the compressor outlet port 26, a first throttling valve 46 located between the condenser 44 and a flash chamber 48, which in turn is connected on the gas side to the intermediate pressure supply opening 38 of the compressor and on the liquid side to a second throttling valve 50, and an evaporator 52 connected to the second throttling valve 50 and the low pressure compressor inlet 24.
- the built-in volume ratio (V i ) is shown as a function of the position (L) of the control edge 34 when moving from the position for maximum capacity to the position for minimum capacity, where a fixed edge of the axial portion may decide the size of the outlet port 26.
- the built-in volume ratio will be kept practically constant at all capacities which means that the efficiency of the compressor can be kept on a high level over a wide field of part load capacity, simultaneously as the so called "economizer" effect is maintained at an optimum level.
- the corresponding function for compressors as shown in Swedish patent 382 663 and in US patent 3 568 466, supplemented by a conventional capacity valve as shown in US patent 3 314 597, respectively.
- thermodynamical process within the plant shown in Fig. 3 is indicated in Fig. 5 as a diagram showing the relation between the pressure (log p) and the enthalpy (i).
- the different points thereof related to specific details indicated in the plant shown in Fig. 3 has been denoted by the same reference numbers.
- the line 42 corresponds to the compressor, with its inlet port, additional supply opening, and outlet port at point 24, 38 and 26, respectively.
- Line 44 corresponds to the condenser
- point 46 corresponds to the first throttling valve
- point 48 to the flash chamber
- point 50 corresponds to the second throttling valve
- line 52 corresponds to the evaporator.
- the process drawn in continuous lines indicates the process at full load and at part load according to the invention.
- the invention thus results not only in an improved compressor efficiency but also when used in a refrigeration plant in an improved process efficiency, which means a considerably higher total efficiency of the plant.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
- The present invention relates to a screw compressor, especially adapted for use within a refrigeration plant with two stage throttling. Such a compressor comprises a casing with a working space generally composed of intersecting bores with parallel axes enclosed by barrel and end walls and provided with spaced apart inlet and outlet ports for communication with inlet and outlet channels, respectively. Rotors, each having helical lands and intervening grooves, are disposed in the bores and intermesh in pair. One rotor of the pair is of male rotor type formed such that at least the major portion of each land and groove is located outside the pitch circle of the rotor. The other rotor is of female rotor type formed such that at the major portion of each land and groove is located inside the pitch circle of the rotor. Two communicating groove portions thus form a chevron-shaped chamber having its base end disposed in a plane transverse to the axes of the bores and adjacent to the outlet port. The compressor is provided with capacity control means comprising a bleed port and a valve member having an axially displaceable control edge defining the actual size of the port. The compressor is further provided with means for additional supply of working fluid at a pressure higher than the normal inlet pressure.
- A compressor of the above type for use in a refrigeration plant is known from Swedish patent 382 663. This compressor is provided with an axially slidable valve of the type shown in Swedish patent 366 375, i.e. a valve member disposed in the barrel wall of the working space and including the intersection line between the bores so that the valve simultaneously adjusts a bleed port at one end and the outlet port at the other end. This valve member is provided with openings, for additional supply of gas from the first throttling stage, situated so that at maximum capacity the openings are disposed on such a distance from the inlet end wall that they communicate with a chevron-shaped chamber first after the initiation of the compression. By this compressor construction it is possible to achieve a certain "economizer" effect even at part load.
- However, the construction shown in Swedish patent 382 663 involves problems and disadvantages not discussed in the patent. A valve member of the type shown decreases for a certain displacement thereof the outlet volume, i.e. the volume of the chevron-shaped chamber when opening towards the outlet port, and the inlet volume, i.e. the volume of the chevron-shaped chamber when cut off from the bleed port, with the same quantity. The ratio between the inlet volume and the outlet volume, the built-in volume ratio, thus increases with increasing bleed off. This effect is further accentuated when additional working fluid is supplied after the cut off from the bleed port. In order to avoid too high built-in volume ratios and over-compression resulting therefrom the bleed port must when opened momentarily mean a considerable reduction of the inlet volume eventhough this on the other hand means a low built-in volume ratio resulting in under-compression. The possibility to vary the volumetric capacity of a compressor without too high losses in the adiabatic efficiency is thus limited. With additional supply openings in the valve member there is a further problem that those openings in order to maintain a higher pressure therein than the inlet pressure must be located on a considerable distance from the edge thereof controlling the bleed port. Consequently the bleed port in such a compressor must be situated closer to the inlet end wall than in normal compressors. In other words the reduction of the inlet volume when opening the bleed port can only be a fraction of that in earlier known compressors and consequently the range for variation of the volumetric capacity will be further reduced.
- The object of the present invention is to provide a compressor of the type specified where the range of capacity variation with high adiabatic efficiency is considerably extended simultaneously as the intermediate, additional supply pressure is on a steady high level required for an optimum process, which means that the over-all efficiency of the plant at part load is kept on a much higher level than that obtained by earlier used compressors.
- This object is met according to the invention in that said capacity control means is situated peripherally out of the outlet port, that said additional supply means comprises a port within said capacity control valve located at an axial distance from said control edge at least corresponding to the axial distance between two consecutive lands of the facing rotor, and that separate means are provided for selective adjustment of the outlet port.
- A further improvement of the efficiency of the compressor may be obtained by providing the outlet port valve with injection means for a cooling and sealing liquid, said injection means being located such that it never communicates with any of the inlet and outlet ports or with the additional supply means, at least at low capacity reduction conditions.
- An embodiment of the invention will now be described by way of example with reference to the accompanying drawings, in which
- Fig. 1 shows a transverse section of a screw compressor taken along line 1 - 1 in Fig. 2,
- Fig. 2 shows a developed view of the barrel wall of a screw compressor taken along line 2 - 2 in Fig. 1,
- Fig. 3 shows diagrammatically a refrigeration plant with two stage throttling and a compressor according to Figs. 1 and 2,
- Fig. 4 shows diagrammatically the built-in volume ratio of a compressor as shown in Figs. 1 and 2 as a function of the position of the capacity valve, and
- Fig. 5 shows diagrammatically the thermodynamical process within a plant as shown in Fig. 4.
- The compressor shown in Figs. 1 and 2 comprises a
male rotor 10 provided with fivehelical lands 12 and intervening grooves 14-and afemale rotor 16 intermeshing therewith and provided with sixhelical lands 18 each enclosing a rotor and interveninggrooves 20. Therotors barrel member 22 comprising two intersecting bores each enclosing a rotor. The housing is provided with aninlet port 24 at the low pressure end and extending as a relieved portion into the barrel wall and anoutlet port 26 at the high pressure end. In thebarrel member 22 there are further two circular grooves intersecting with the barrel wall and each enclosing an axiallyadjustable valve member rotor outlet port 26 and a pressure adjustingvalve member 28 enclosed therein is provided with a control edge 32 defining the actual shape and size of theoutlet port 26. The other valve groove is located in the wall of the bore enclosing themale rotor 10, peripherally out of the area of theoutlet port 26 and encloses a capacity adjustingvalve member 30 provided with acontrol edge 34 facing theinlet port 24 and at full capacity defining a part of the edge thereof, whereas at reduced capacity this edge defines the size and shape of ableed port 36 communicating with theinlet port 24. Thecapacity valve 30 is further provided with anopening 38 for supply of additional working fluid at an intermediate pressure higher than that of the fluid supplied through theinlet port 24. Thisadditional supply opening 38 is located at an axial distance from thecontrol edge 34 corresponding to the axial distance between twoconsecutive lands 12 of the facingrotor 10. Thepressure valve 28 is similarly provided with anopening 40 for supply of a cooling and sealing liquid, which in a refrigeration compressor may consist of liquefied working fluid preferably having a temperature below the condensing temperature, which will improve the efficiency of the compressor. In Fig. 3 a refrigeration plant is shown, which comprises acompressor 42 of the type specified above, acondenser 44 connected to thecompressor outlet port 26, afirst throttling valve 46 located between thecondenser 44 and aflash chamber 48, which in turn is connected on the gas side to the intermediate pressure supply opening 38 of the compressor and on the liquid side to asecond throttling valve 50, and anevaporator 52 connected to thesecond throttling valve 50 and the lowpressure compressor inlet 24. - In Fig. 4 the built-in volume ratio (Vi) is shown as a function of the position (L) of the
control edge 34 when moving from the position for maximum capacity to the position for minimum capacity, where a fixed edge of the axial portion may decide the size of theoutlet port 26. As can be seen from the continuous line the built-in volume ratio will be kept practically constant at all capacities which means that the efficiency of the compressor can be kept on a high level over a wide field of part load capacity, simultaneously as the so called "economizer" effect is maintained at an optimum level. As a comparison are also the corresponding function for compressors as shown in Swedish patent 382 663 and in USpatent 3 568 466, supplemented by a conventional capacity valve as shown in USpatent 3 314 597, respectively. - The conditions in a compressor according to Swedish patent 382 663, where the additional supply openings are located in a conventional capacity valve, is shown by a dotted line. As the intermediate pressure at maximum capacity is fixed and due to the fact that the supply openings must be located on a considerable distance from the edge of the valve controlling the bleed port which in turn means that the position "a" of this edge at full load must be situated close to the low pressure end of the compressor. At the moment when the bleed port is opened the inlet volume will be abruptly reduced whereas the outlet volume at the outlet port will be practically constant which means that the built-in volume ratio decreases momentarily. As the valve is moved further on towards lower compressor capacity the inlet and outlet volumes will be reduced by the same amount. This means, however, a relatively low reduction of the inlet volume percentagewise and a high reduction of the outlet volume percentagewise which means that the built-in volume ratio increases rapidly and the more the valve is moved the faster the built-in volume ratio increases up to the point where the edge of the axial portion of the outlet port takes over as deciding factor for the outlet volume. After that point the inlet volume continues to decrease, whereas the outlet volume is kept constant and consequently the built-in volume ratio starts to decrease once more. Over the range where the built-in ratio thus is higher than that at full load the working fluid will be overcompressed resulting in considerable increase of the power required and consequently a decreased efficiency. Owing to the fact that a too high built-in volume ratio cannot be accepted the field for capacity variation will thus be rather limited simultaneously as the part load efficiency will be poor.
- The conditions in a capacity controlled compressor according to US
patent 3 568 466, where the additional supply openings are fixed and located in the wall of the compressor housing, is shown by a point-dotted line. In order to obtain an acceptable width of the capacity variation range the bleed port controlling edge of the valve is located on a considerable distance from the low pressure end of the compressor. The position of this edge at full load is in the diagram indicated by "b". The variation of the built-in volume ratio with the capacity will in principle be the same as that discussed above with regard to the compressor according to Swedish patent 382 663. However, as the valve control edge is located further away from the low pressure end of the compressor the abrupt reduction of the inlet volume, at the moment when the bleed port is opened, is considerably larger the drop in the built-in volume ratio will also be larger which on the other hand means that the increase of said ratio, as the valve is moved further on, will be less steep. Over a considerable capacity range the built-in volume ratio will thus be within reasonable limits from the ideal value. During the first part of the capacity range the ratio will be lower than the ideal, which means under- compression and consequently a completion of the compression will be by full back pressure compression, which means a loss and consequently a decreased efficiency. - Already from this point of view the invention thus means a considerable improvement over the prior art.
- The thermodynamical process within the plant shown in Fig. 3 is indicated in Fig. 5 as a diagram showing the relation between the pressure (log p) and the enthalpy (i). In the diagram the different points thereof related to specific details indicated in the plant shown in Fig. 3 has been denoted by the same reference numbers. Thus the
line 42 corresponds to the compressor, with its inlet port, additional supply opening, and outlet port atpoint Line 44 corresponds to the condenser,point 46 corresponds to the first throttling valve, thepoint 48 to the flash chamber,point 50 corresponds to the second throttling valve, andline 52 corresponds to the evaporator. The process drawn in continuous lines indicates the process at full load and at part load according to the invention. In this process the flash gas from the first stage throttling is only compressed from the pressure inpoint 38 topoint 26 which means a considerable reduction of the power consumption and thus an improvement of the process compared with a system with single stage throttling where all flash gas has to be compressed frompoint 24 topoint 26. This is the so called "economizer effect". When using a compressor of the type shown in Swedish patent 382 663 at part load the intermediate pressure drops which in combination with overcompression results in a change of the process as indicated by dotted lines andpoints US patent 3 568 466 supplemented by a standard valve at part load the intermediate pressure drops down to evaporator pressure, simultaneously as the compressor acts with over- or undercompression. The process including undercompression is indicated by point-dotted lines and points 48b, 50b, 38b and 26b. - The invention thus results not only in an improved compressor efficiency but also when used in a refrigeration plant in an improved process efficiency, which means a considerably higher total efficiency of the plant.
Claims (5)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB858528211A GB8528211D0 (en) | 1985-11-15 | 1985-11-15 | Screw compressor |
GB8528211 | 1985-11-15 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0245427A1 EP0245427A1 (en) | 1987-11-19 |
EP0245427B1 true EP0245427B1 (en) | 1989-10-04 |
Family
ID=10588296
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19860906989 Expired EP0245427B1 (en) | 1985-11-15 | 1986-11-14 | Screw rotor compressor and refrigeration plant |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0245427B1 (en) |
AU (1) | AU6732287A (en) |
DE (1) | DE3666074D1 (en) |
GB (1) | GB8528211D0 (en) |
WO (1) | WO1987003048A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5228301A (en) * | 1992-07-27 | 1993-07-20 | Thermo King Corporation | Methods and apparatus for operating a refrigeration system |
US5246357A (en) * | 1992-07-27 | 1993-09-21 | Westinghouse Electric Corp. | Screw compressor with oil-gas separation means |
WO2008112554A1 (en) * | 2007-03-09 | 2008-09-18 | Johnson Controls Technology Company | Refrigeration system |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NO117317B (en) * | 1964-03-20 | 1969-07-28 | Svenska Rotor Maskiner Ab | |
SE338576B (en) * | 1968-05-06 | 1971-09-13 | Stal Refrigeration Ab | |
SE366375B (en) * | 1972-06-30 | 1974-04-22 | Stal Refrigeration Ab | |
SE382663B (en) * | 1974-04-11 | 1976-02-09 | Stal Refrigeration Ab | PROCEED TO INSERT INTERMEDIATE PRESSURE GAS INTO A SCREW COOLER COMPRESSOR AND SCREW COMPRESSOR FOR PERFORMING THE KIT. |
-
1985
- 1985-11-15 GB GB858528211A patent/GB8528211D0/en active Pending
-
1986
- 1986-11-14 DE DE8686906989T patent/DE3666074D1/en not_active Expired
- 1986-11-14 EP EP19860906989 patent/EP0245427B1/en not_active Expired
- 1986-11-14 WO PCT/SE1986/000526 patent/WO1987003048A1/en active IP Right Grant
- 1986-11-14 AU AU67322/87A patent/AU6732287A/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
AU6732287A (en) | 1987-06-02 |
GB8528211D0 (en) | 1985-12-18 |
EP0245427A1 (en) | 1987-11-19 |
WO1987003048A1 (en) | 1987-05-21 |
DE3666074D1 (en) | 1989-11-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0259333B1 (en) | Refrigeration plant and rotary positive displacement machine | |
EP0419531B1 (en) | Rotary positive displacement compressor and refrigeration plant | |
US4351160A (en) | Capacity control systems for screw compressor based water chillers | |
US3088658A (en) | Angularly adjustable slides for screw rotor machines | |
US3568466A (en) | Refrigeration system with multi-stage throttling | |
US4005949A (en) | Variable capacity rotary screw compressor | |
EP1158167B1 (en) | Air conditioner with scroll compressor | |
US5150581A (en) | Head pressure controller for air conditioning and refrigeration systems | |
EP0350426B1 (en) | Common compression zone access ports for positive displacement compressor | |
US5082427A (en) | Screw compressing apparatus, rotor temperature control apparatus for screw compressing apparatus and operating control apparatus for screw compressing apparatus | |
EP1573203B1 (en) | Screw compressor with axially sliding capacity control valve | |
WO1989003482A1 (en) | Rotary displacement compressor | |
US4611976A (en) | Capacity and internal compression control device in a screw compressor | |
CA2885727C (en) | Apparatus and method for enhancing compressor efficiency | |
US4534719A (en) | Volumetric screw-and-pinion machine and a method for using the same | |
US4455131A (en) | Control device in a helical screw rotor machine for regulating the capacity and the built-in volume ratio of the machine | |
EP0245427B1 (en) | Screw rotor compressor and refrigeration plant | |
US3859814A (en) | Variable capacity rotary screw compressor | |
US4457681A (en) | Volume ratio control means for axial flow helical screw type compressor | |
SU873894A3 (en) | Screw compressor with controlled discharge | |
US6422846B1 (en) | Low pressure unloader mechanism | |
EP0564123A1 (en) | Refrigeration system | |
US20040234381A1 (en) | Screw compressor capable of manually adjusting both internal volume ratio and capacity and combined screw compressor unit accommodating variation in suction or discharge pressure | |
JPH021998B2 (en) | ||
SU962673A1 (en) | Screw compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH DE FR GB IT LI LU NL SE |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SVENSKA ROTOR MASKINER AB |
|
17P | Request for examination filed |
Effective date: 19871012 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SVENSKA ROTOR MASKINER AB |
|
RBV | Designated contracting states (corrected) |
Designated state(s): BE DE FR GB IT NL SE |
|
17Q | First examination report despatched |
Effective date: 19880714 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): BE DE FR GB IT NL SE |
|
REF | Corresponds to: |
Ref document number: 3666074 Country of ref document: DE Date of ref document: 19891109 |
|
ITF | It: translation for a ep patent filed |
Owner name: BARZANO' E ZANARDO MILANO S.P.A. |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
ITTA | It: last paid annual fee | ||
EAL | Se: european patent in force in sweden |
Ref document number: 86906989.8 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20031027 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20031030 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20031111 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20031118 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20031124 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20031126 Year of fee payment: 18 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20041114 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20041115 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20041130 |
|
BERE | Be: lapsed |
Owner name: *SVENSKA ROTOR MASKINER A.B. Effective date: 20041130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050601 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050601 |
|
EUG | Se: european patent has lapsed | ||
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20041114 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050729 |
|
NLV4 | Nl: lapsed or anulled due to non-payment of the annual fee |
Effective date: 20050601 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20051114 |
|
BERE | Be: lapsed |
Owner name: *SVENSKA ROTOR MASKINER A.B. Effective date: 20041130 |