EP2264319B1 - Oil free screw compressor - Google Patents
Oil free screw compressor Download PDFInfo
- Publication number
- EP2264319B1 EP2264319B1 EP10164131.4A EP10164131A EP2264319B1 EP 2264319 B1 EP2264319 B1 EP 2264319B1 EP 10164131 A EP10164131 A EP 10164131A EP 2264319 B1 EP2264319 B1 EP 2264319B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotors
- rotor
- casing
- screw compressor
- slot
- 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.)
- Active
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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/086—Carter
-
- 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
-
- 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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
-
- 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
- F04C29/06—Silencing
- F04C29/065—Noise dampening volumes, e.g. muffler chambers
-
- 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
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
-
- 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
-
- 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
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/102—Geometry of the inlet or outlet of the outlet
Definitions
- the present invention relates to an oil free screw compressor in which oil is prevented from entering a compression chamber formed by a pair of male screw rotor and a female screw rotor, such as disclosed in US5413467 .
- screw compressors There are two types of screw compressors in which a pair of screw rotors are combined to form a compression chamber.
- One is an oil-injected screw compressor in which a lubricating oil is supplied to a compression chamber in order to cool the compressor and to enable the smooth drive of the pair of rotors.
- the other is an oil free screw compressor which avoids the contact of a pair of rotors by driving them via timing gears and prevents oil from entering a compression chamber.
- Japanese Patent Unexamined Publication No. 63-45488 discloses an example of the conventional oil free screw compressor described above. According to the screw compressor of Japanese Patent Unexamined Publication No. 63-45488 , in order to avoid a problem that the power of the compressor increases when part of the cooled discharge gas is returned to a suction side, at a portion closer to the discharge port side than a position of a wall part of a rotor chamber in communication with the discharge port and, at the same time, in a space of the rotor chamber near the discharge port or at the discharge port immediately after the start of discharging, branch passages branched on the exit side of discharge gas cooling means in the discharge passage is allowed to merge.
- Japanese Patent Unexamined Publication No. 2008-82273 an example of the oil-injected screw compressor is described in Japanese Patent Unexamined Publication No. 2008-82273 .
- a recess is formed in a wall face opposed to an end face on the rotor discharge side of a casing. Further, a compression chamber is brought into communication with the recess immediately before the compression chamber is isolated from the discharge port and such communication is kept until a volume of the compression chamber becomes substantially zero.
- the oil-injected screw compressor permits a lubricating oil given to bearings to enter the compression chamber, and oil is separated outside the compressor. Therefore, a main body of the compressor is simply structured.
- the oil free screw compressor requires a highly efficient shaft sealing apparatus. As a result, since the rotor becomes longer, in order to suppress vibration in a high-speed rotating apparatus, a length of the casing in a depth direction of the end face is considerably restricted.
- the present invention is made in view of the above problems of the conventional art. Therefore, an object of the present invention is to prevent the problems, in an oil free screw compressor, such as excessive compression etc. which might be caused by closing of the discharge port before a volume of the compression chamber becomes zero. Another object of the present invention is to suppress an increase in power consumption caused by the excessive compression etc. or an excessive rise in temperature of the compressed air. Still another object of the present invention is to realize a discharge port capable of efficiently discharging a compressed air from the discharge port until the timing with which the volume of the compression chamber becomes zero with use of inexpensive manufacturing means. The present invention aims to achieve at least one of the objects described above.
- an oil free screw compressor which may in particular comprise: a pair of male and female screw rotors in which two or more twisted teeth are formed; a casing which receives both the rotors and in which a suction port and a discharge port are formed; bearings which rotatably support shaft end parts of both the rotors and are held in the casing; timing gears which are mounted on one shaft end part of both the rotors and which allow both the rotors to rotate in synchronism without contacting with each other; and a shaft sealing apparatus which is disposed between each of the bearings and teeth of the rotors and which prevents oil from entering a meshing portion of the rotors, wherein there is provided a slot, next to the discharge port of the casing, which comes into communication with the discharge port with timing where a volume of a compression chamber formed by both the rotors and the casing becomes substantially zero as both the
- the slot extends from a periphery of a position where a tooth bottom circle of the female rotor overlaps with a tooth top circle of the male rotor to a line which connects centers of both the rotors. Further, the slot extends outward from a tooth top part of the male rotor and its width is greater than its depth in an axial direction. Still further, the slot is preferably formed by cutting to prevent the leak from a discharge side to a suction side.
- the present invention on the oil free screw compressor, there is provided means to be in communication with the discharge port until the volume of the compression chamber becomes substantially zero, which can prevent problems such as excessive compression etc. and can also suppress an increase in power consumption to be caused by the excessive compression etc. or an excessive rise in temperature of the compressed air. Further, it is possible to efficiently discharge the compressed air from the discharge port until the timing with which the volume of the compression chamber becomes zero with use of an inexpensive manufacturing method.
- Fig. 5(a) is the top cross sectional view of the oil free screw compressor 50 and Fig. 5(b) is the front cross sectional view.
- the oil free screw compressor 50 has a pair of male screw rotor 1 and a female screw rotor 2, which are received in bores formed in a casing 3.
- the bores are structured such that two cylindrical spaces are provided next to each other in a direction orthogonal to the axial direction, and their shaft centers are in parallel with each other.
- Shaft ends on one side of the rotors 1 and 2 are rotatably supported by bearings 11 and 12, and shaft ends on the other side are rotatably supported by bearings 13 and 14.
- the bearings 11 to 14 are held in the casing 3.
- a lubricating oil is supplied to the bearings 11 to 14.
- the screw compressor 50 according to the present invention is an oil free compressor. Therefore, in order to prevent the lubricating oil from entering a compression chamber to be described later, shaft sealing apparatuses 31 to 34 are provided closer to a central side than bearings in the axial direction.
- a pinion gear 21 is mounted on one shaft end of the female rotor 2, and the pinion gear 21 engages with a motor (not shown).
- Timing gears 22 and 23 are mounted on the male and female rotors 1 and 2. The male and female rotors rotate in synchronism through both the timing gears 22 and 23 engaging with each other.
- Middle portions of the male and female rotors 1 and 2 in the axial direction have large diameters.
- the large-diameter portions of the rotors 1 and 2 are held with little clearances between themselves and inner wall surfaces of the bores formed in the casing 3.
- the male rotor 1 has four teeth and the female rotor 2 has six slots. While keeping a little clearance, the teeth of the male rotor 1 engage with the slots of the female rotor 2.
- a suction port which leads the air taken in through the suction port to the compression chamber formed by both the rotors 1 and 2 and the casing 3.
- a discharge port 4 which leads the compressed air from the compression chamber formed by both the rotors 1 and 2 and the casing 3 to the outside of the compressor.
- Fig. 2 is a cross sectional view taken in the direction of arrows along line A-A of Fig. 1 and shows a periphery of the discharge port of the male rotor 1.
- Fig. 3 is a cross sectional view taken in the direction of arrows along line B-B of Fig. 2 and shows a portion where the male and female rotors 1 and 2 engage with each other and a periphery of the discharge port 4.
- Fig. 4 is a cross sectional view taken in the direction of arrows along line C-C of the periphery of the portion where the male and female rotors 1 and 2 engage with each other and shows a horizontal cross section.
- the oil free screw compressor 50 air is introduced into the casing 3 through a suction pipe. Then, as the rotors 1 and 2 rotate, a volume of the compression chamber formed by the pair of male and female rotors 1 and 2 and the casing 3 receiving both the rotors 1 and 2 is expanded and taken inside the compressor. Subsequently, the compression chamber is completely closed by the casing 3 around a point where the compression chamber comes to have a maximum volume. As the rotors 1 and 2 further rotate, the compression chamber is contracted, thereby raising the air pressure.
- the discharge port is formed in accordance with tooth profiles of the rotors 1 and 2 in an end face portion in the axial direction of the rotors 1 and 2 near the outer-diameter part.
- the compressed air is discharged from this discharge port.
- clearances are formed so that they do not come into contact with each other. In the oil free screw compressor 50, when air escapes through the clearances, its performance is degraded.
- the shape of the casing 3 cannot help becoming complex, and the casing is generally made by casting.
- the suction port and the discharge port are also formed by casting. However, a portion which has to be made with high precision is produced by machining.
- the discharge port 4 in order to avoid an increase in power consumption due to excessive compression and a rise in temperature of compressed air, it is desirable to form an opening so that the compressed air can be discharged until the timing with which the volume of the compression chamber becomes zero.
- the excessive compression can be prevented by the above conventional method. However, since the compressed air constantly escapes from the end face, the performance is inevitably degraded. In view of the above, according to the present invention, the excessive compression is also prevented while reducing the leak from the end face with use of a simple structure.
- the male rotor 1 and the female rotor 2 are regarded to be in contact through respective tooth faces.
- the clearances are formed to such an extent as the tooth faces not coming into contact with each other even when thermal expansion is taken into account.
- the clearances are very small. Therefore, in substantial consideration, it may be regarded that the tooth faces come into contact with each other.
- DIR indicates a direction in which the rotors 1 and 2 rotate.
- an advance face SF1 which is a tooth face of the male rotor 1 and a face which first comes into contact with a tooth 8sur) face of the female rotor 2
- a tooth face SF2 of the female rotor 2 which forms a compression chamber 7 between themselves and an inner wall face of the casing 3.
- the compression chamber 7 moves to a discharge side from a suction side in the axial direction.
- the compression chamber is divided by an imaginary contact line called a seal line between the male rotor 1 and the female rotor 2.
- a seal line between the male rotor 1 and the female rotor 2.
- the male rotor 1 and the female rotor 2 are in contact with each other at points P1, P2, and P3 on the tooth face.
- the compression chamber is formed between the advance face SF1, whose both ends are partitioned by the points P1 and P2, of the male rotor 1 and the tooth face SR2 of the female rotor 2.
- another compression chamber 8 is formed by the tooth face SR1 opposed to an advance face PF1 of the male rotor 1, the advance face SF2 of the female rotor 2, and the points P2 and P3.
- the discharge port is formed corresponding to the change in the shape of the compression chamber.
- a discharge passage 31 for connection to the compression chamber is formed near an end face on the discharge side of the rotors 1 and 2 in a lower portion of the casing 3. As shown by a dashed line in Fig.
- a side wall portion of the casing 3 is opened to a profile formed by the anti-advance face SR1 of a tooth which engages after the male rotor 2, a tooth bottom circle of the male rotor 2, the face SR2 opposite to the advance face of the teeth which engage after the female rotor 2, a tooth bottom circle of the female rotor 2, and tooth top circles of the male and female rotors 1 and 2.
- a discharge port processing slot 6 is formed so as to be able to discharge compressed air even when the volume of the compression chamber becomes substantially zero.
- the processing slot 6 will be explained in detail below.
- the processing slot 6 is located near a meshing portion of a tooth top of the male rotor 1 and a tooth bottom of the female rotor 2.
- the processing slot 6 is located on an outer side of the male rotor 1 than the outer diameter of the tooth top so that the discharge port 4 does not come into communication with the compression chamber 8 in a state of being ready for suction.
- the processing slot 6 is positioned outside the outer diameter of the tooth top of the male rotor 1 by a clearance of about d (see Fig. 2 ) between the end face of the rotor 1 on the discharge side and the casing 3.
- a width of the processing slot 6 is made to be as small as possible.
- the depth of the processing slot 6, namely, a dimension e in the axial direction is restricted because the shaft sealing apparatus 34 is provided, it may be about half the width d of the slot (see Fig. 4 ).
- a length W of the processing slot 6 is set to be from a corner portion of the above described discharge port 4, namely, a portion where the tooth bottom part of the female rotor 2 overlaps with the tooth top part of the male rotor 1 to a line which connects the shaft centers of the male rotor 1 and the female rotor 2.
- the processing slot 6 is defined as described above because of the following reasons: If the length W of the processing slot 6 is longer than that, namely, if it exceeds the line connecting the centers of the male rotor 1 and the female rotor 2, it joins with a slot for starting suction. Therefore, the compressed air is returned to the suction side. Also, the depth e of the processing slot is defined by taking workability into consideration. Further, if the width d of the processing slot 6 is widened excessively, the slot becomes too close to a hole of the shaft sealing part of the female rotor 2 and the compressed air flows into the shaft sealing part. Because of these reasons, the dimension of the processing slot 6 is defined as above.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
- The present invention relates to an oil free screw compressor in which oil is prevented from entering a compression chamber formed by a pair of male screw rotor and a female screw rotor, such as disclosed in
US5413467 . - There are two types of screw compressors in which a pair of screw rotors are combined to form a compression chamber. One is an oil-injected screw compressor in which a lubricating oil is supplied to a compression chamber in order to cool the compressor and to enable the smooth drive of the pair of rotors. The other is an oil free screw compressor which avoids the contact of a pair of rotors by driving them via timing gears and prevents oil from entering a compression chamber.
- In industrial fields such as electronics, food, and chemistry where mixing of oil is regarded unfavorable, there is a great demand for oil free screw compressors. However, it is said that an electric power expense of an air compressor occupies as much as about 25% of electric power expenses in a plant facility. Therefore, a compressor with little power consumption and high energy efficiency is called for.
- Japanese Patent Unexamined Publication No.
63-45488 63-45488 - Further, although it is not an oil free screw compressor, an example of the oil-injected screw compressor is described in Japanese Patent Unexamined Publication No.
2008-82273 2008-82273 - In the oil free screw compressor according to Japanese Patent Unexamined Publication No.
63-45488 63-45488 - Moreover, the oil-injected screw compressor according to Japanese Patent Unexamined Publication No.
2008-82273 - Further, when the invention as it is disclosed by Japanese Patent Unexamined Publication No.
2008-82273 - The present invention is made in view of the above problems of the conventional art. Therefore, an object of the present invention is to prevent the problems, in an oil free screw compressor, such as excessive compression etc. which might be caused by closing of the discharge port before a volume of the compression chamber becomes zero. Another object of the present invention is to suppress an increase in power consumption caused by the excessive compression etc. or an excessive rise in temperature of the compressed air. Still another object of the present invention is to realize a discharge port capable of efficiently discharging a compressed air from the discharge port until the timing with which the volume of the compression chamber becomes zero with use of inexpensive manufacturing means. The present invention aims to achieve at least one of the objects described above.
- In order to achieve the above described object, according to a feature of the present invention, there is provided an oil free screw compressor according to
claim 1, which may in particular comprise: a pair of male and female screw rotors in which two or more twisted teeth are formed; a casing which receives both the rotors and in which a suction port and a discharge port are formed; bearings which rotatably support shaft end parts of both the rotors and are held in the casing; timing gears which are mounted on one shaft end part of both the rotors and which allow both the rotors to rotate in synchronism without contacting with each other; and a shaft sealing apparatus which is disposed between each of the bearings and teeth of the rotors and which prevents oil from entering a meshing portion of the rotors, wherein there is provided a slot, next to the discharge port of the casing, which comes into communication with the discharge port with timing where a volume of a compression chamber formed by both the rotors and the casing becomes substantially zero as both the rotors rotate. - In regard to the above feature, the slot extends from a periphery of a position where a tooth bottom circle of the female rotor overlaps with a tooth top circle of the male rotor to a line which connects centers of both the rotors. Further, the slot extends outward from a tooth top part of the male rotor and its width is greater than its depth in an axial direction. Still further, the slot is preferably formed by cutting to prevent the leak from a discharge side to a suction side.
- According to the present invention, on the oil free screw compressor, there is provided means to be in communication with the discharge port until the volume of the compression chamber becomes substantially zero, which can prevent problems such as excessive compression etc. and can also suppress an increase in power consumption to be caused by the excessive compression etc. or an excessive rise in temperature of the compressed air. Further, it is possible to efficiently discharge the compressed air from the discharge port until the timing with which the volume of the compression chamber becomes zero with use of an inexpensive manufacturing method.
-
-
Fig. 1 is a transverse cross sectional view showing a principal part of one embodiment of an oil free screw compressor according to the present invention; -
Fig. 2 is a cross sectional view taken along line A-A ofFig. 1 ; -
Fig. 3 is a cross sectional view taken along line B-B ofFig. 1 ; -
Fig. 4 is a cross sectional view taken along line C-C ofFig. 1 ; and -
Figs. 5(a) and 5(b) are a top cross sectional view and a front cross sectional view of one embodiment of the oil free screw compressor of the present invention. - With reference to the drawings, one embodiment of the oil free screw compressor of the invention will be described. First, with reference to
Figs. 5 (a) and 5(b) , an outline of the oil free screw compressor will be explained.Fig. 5(a) is the top cross sectional view of the oilfree screw compressor 50 andFig. 5(b) is the front cross sectional view. The oilfree screw compressor 50 has a pair ofmale screw rotor 1 and afemale screw rotor 2, which are received in bores formed in acasing 3. The bores are structured such that two cylindrical spaces are provided next to each other in a direction orthogonal to the axial direction, and their shaft centers are in parallel with each other. - Shaft ends on one side of the
rotors bearings bearings bearings 11 to 14 are held in thecasing 3. A lubricating oil is supplied to thebearings 11 to 14. Thescrew compressor 50 according to the present invention is an oil free compressor. Therefore, in order to prevent the lubricating oil from entering a compression chamber to be described later,shaft sealing apparatuses 31 to 34 are provided closer to a central side than bearings in the axial direction. - A
pinion gear 21 is mounted on one shaft end of thefemale rotor 2, and thepinion gear 21 engages with a motor (not shown).Timing gears female rotors timing gears - Middle portions of the male and
female rotors rotors casing 3. On the large-diameter portions of therotors male rotor 1 has four teeth and thefemale rotor 2 has six slots. While keeping a little clearance, the teeth of themale rotor 1 engage with the slots of thefemale rotor 2. - On one side (right side in
Fig. 5 ) of themale rotor 1 and thefemale rotor 2, there is formed a suction port which leads the air taken in through the suction port to the compression chamber formed by both therotors casing 3. On the opposite side of both therotors discharge port 4 which leads the compressed air from the compression chamber formed by both therotors casing 3 to the outside of the compressor. - With reference to a transverse cross sectional view of the
screw compressor 50 inFig. 1 and Figs. 2 and4 showing cross sections of parts inFig. 1 , thedischarge port 4 will be explained in detail.Fig. 2 is a cross sectional view taken in the direction of arrows along line A-A ofFig. 1 and shows a periphery of the discharge port of themale rotor 1.Fig. 3 is a cross sectional view taken in the direction of arrows along line B-B ofFig. 2 and shows a portion where the male andfemale rotors discharge port 4.Fig. 4 is a cross sectional view taken in the direction of arrows along line C-C of the periphery of the portion where the male andfemale rotors - In the oil
free screw compressor 50, air is introduced into thecasing 3 through a suction pipe. Then, as therotors female rotors casing 3 receiving both therotors casing 3 around a point where the compression chamber comes to have a maximum volume. As therotors - Corresponding to a state where the compression chamber is contracted to a predetermined volume, the discharge port is formed in accordance with tooth profiles of the
rotors rotors male rotor 1 and thefemale rotor 2 as well as between both therotors casing 3, clearances are formed so that they do not come into contact with each other. In the oilfree screw compressor 50, when air escapes through the clearances, its performance is degraded. Therefore, when the clearances are made as small as possible, its performance is improved. Even so, the shape of thecasing 3 cannot help becoming complex, and the casing is generally made by casting. The suction port and the discharge port are also formed by casting. However, a portion which has to be made with high precision is produced by machining. - In particular, as for the
discharge port 4, in order to avoid an increase in power consumption due to excessive compression and a rise in temperature of compressed air, it is desirable to form an opening so that the compressed air can be discharged until the timing with which the volume of the compression chamber becomes zero. However, it is difficult to form the opening by casting or machining. Also, it may increase the manufacturing cost. Therefore, the clearances are allowed in the end faces of therotors - The excessive compression can be prevented by the above conventional method. However, since the compressed air constantly escapes from the end face, the performance is inevitably degraded. In view of the above, according to the present invention, the excessive compression is also prevented while reducing the leak from the end face with use of a simple structure.
- Since the explanation below is a theoretical one, the
male rotor 1 and thefemale rotor 2 are regarded to be in contact through respective tooth faces. As described above, in the actual oil free screw compressor, when tooth faces come into contact with each other, friction, wear, vibration, and noise are caused. Therefore, clearances are formed to such an extent as the tooth faces not coming into contact with each other even when thermal expansion is taken into account. However, the clearances are very small. Therefore, in substantial consideration, it may be regarded that the tooth faces come into contact with each other. - In
Fig. 1 , DIR indicates a direction in which therotors male rotor 1 rotates in synchronism with thefemale rotor 2, an advance face SF1, which is a tooth face of themale rotor 1 and a face which first comes into contact with a tooth 8sur) face of thefemale rotor 2, engages with a tooth face SF2 of thefemale rotor 2, which forms acompression chamber 7 between themselves and an inner wall face of thecasing 3. As the male andfemale rotors compression chamber 7 moves to a discharge side from a suction side in the axial direction. At that time, the compression chamber is divided by an imaginary contact line called a seal line between themale rotor 1 and thefemale rotor 2. When a rear end of the seal line reaches a suction end-wall part 3a of both therotors compression chamber 7 becomes substantially zero.Fig. 1 shows a state where the volume of thecompression chamber 7 has become zero. - That is, the
male rotor 1 and thefemale rotor 2 are in contact with each other at points P1, P2, and P3 on the tooth face. The compression chamber is formed between the advance face SF1, whose both ends are partitioned by the points P1 and P2, of themale rotor 1 and the tooth face SR2 of thefemale rotor 2. On the other hand, anothercompression chamber 8 is formed by the tooth face SR1 opposed to an advance face PF1 of themale rotor 1, the advance face SF2 of thefemale rotor 2, and the points P2 and P3. - In the conventional art, the discharge port is formed corresponding to the change in the shape of the compression chamber. As shown in
Fig. 2 , adischarge passage 31 for connection to the compression chamber is formed near an end face on the discharge side of therotors casing 3. As shown by a dashed line inFig. 2 , a side wall portion of thecasing 3 is opened to a profile formed by the anti-advance face SR1 of a tooth which engages after themale rotor 2, a tooth bottom circle of themale rotor 2, the face SR2 opposite to the advance face of the teeth which engage after thefemale rotor 2, a tooth bottom circle of thefemale rotor 2, and tooth top circles of the male andfemale rotors - Furthermore, according to the present invention, as described above, in order to prevent the excessive compression without degrading the performance, a discharge
port processing slot 6 is formed so as to be able to discharge compressed air even when the volume of the compression chamber becomes substantially zero. Theprocessing slot 6 will be explained in detail below. - As shown in
Fig. 1 , theprocessing slot 6 is located near a meshing portion of a tooth top of themale rotor 1 and a tooth bottom of thefemale rotor 2. In order to prevent the leak of air from the discharge side to the suction side, theprocessing slot 6 is located on an outer side of themale rotor 1 than the outer diameter of the tooth top so that thedischarge port 4 does not come into communication with thecompression chamber 8 in a state of being ready for suction. Furthermore, in order that thecompression chamber 7 in a fully discharged state can be in communication with thedischarge port 4 as much as possible, theprocessing slot 6 is positioned outside the outer diameter of the tooth top of themale rotor 1 by a clearance of about d (seeFig. 2 ) between the end face of therotor 1 on the discharge side and thecasing 3. - In order to reduce the leak of the compressed air to the
shaft sealing apparatus 34 of thefemale rotor 2, a width of theprocessing slot 6 is made to be as small as possible. Although the depth of theprocessing slot 6, namely, a dimension e in the axial direction is restricted because theshaft sealing apparatus 34 is provided, it may be about half the width d of the slot (seeFig. 4 ). A length W of theprocessing slot 6 is set to be from a corner portion of the above describeddischarge port 4, namely, a portion where the tooth bottom part of thefemale rotor 2 overlaps with the tooth top part of themale rotor 1 to a line which connects the shaft centers of themale rotor 1 and thefemale rotor 2. - Specifications of the
processing slot 6 is defined as described above because of the following reasons: If the length W of theprocessing slot 6 is longer than that, namely, if it exceeds the line connecting the centers of themale rotor 1 and thefemale rotor 2, it joins with a slot for starting suction. Therefore, the compressed air is returned to the suction side. Also, the depth e of the processing slot is defined by taking workability into consideration. Further, if the width d of theprocessing slot 6 is widened excessively, the slot becomes too close to a hole of the shaft sealing part of thefemale rotor 2 and the compressed air flows into the shaft sealing part. Because of these reasons, the dimension of theprocessing slot 6 is defined as above. - The above embodiments of the invention as well as the appended claims and figures show multiple characterizing features of the invention in specific combinations. The skilled person will easily be able to consider further combinations or sub-combinations of these features in order to adapt the invention as defined in the in the claims to his specific needs.
Claims (2)
- An oil free screw compressor comprising:a pair of male and female screw rotors (1, 2) in which two or more twisted teeth are formed; a casing (3) which receives both the rotors (1, 2) and in which a suction port and a discharge port are formed; bearings (11 - 14) which rotatably support shaft end parts of said both the rotors (1, 2) and are held in the casing (3) ; timing gears (22, 23) which are mounted on one shaft end part of said both the two rotors (1, 2) and which allow both the rotors (1, 2) to rotate in synchronism without contacting with each other; and a shaft sealing apparatus (31 - 34) which is disposed between each of said bearings (11, 12, 13, 14) and teeth of said rotors (1, 2) and which prevents oil from entering a meshing portion of the rotors (1, 2), characterized in thatwherein there is provided a slot (6), in the casing (3) and outside the outer diameter of the tooth top of the male rotor (1), which comes into communication with the discharge port and with an area formed near a tooth top of the male rotor (1) and a tooth bottom of the female rotor (2), where a volume of a compression chamber (7) formed by both the rotors (1, 2) and the casing (3) becomes substantially zero as said both the rotors (1, 2) rotate, and said slot (6) extends from a periphery of a position where a tooth bottom circle of the female rotor (2) overlaps with a tooth top circle of the male rotor (1) to a line which connects centers of both the rotors (1, 2), wherein said slot (6) extends outward from a tooth top part of said male rotor (1) and its width is greater than its depth in an axial direction.
- The oil free screw compressor according to claim 1, wherein said slot (6) is formed by cutting to prevent the leak from a discharge side to a suction side.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009129389A JP5422260B2 (en) | 2009-05-28 | 2009-05-28 | Oil-free screw compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2264319A2 EP2264319A2 (en) | 2010-12-22 |
EP2264319A3 EP2264319A3 (en) | 2014-05-21 |
EP2264319B1 true EP2264319B1 (en) | 2017-01-11 |
Family
ID=42315405
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10164131.4A Active EP2264319B1 (en) | 2009-05-28 | 2010-05-27 | Oil free screw compressor |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2264319B1 (en) |
JP (1) | JP5422260B2 (en) |
CN (1) | CN101900119B (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102352843A (en) * | 2011-09-26 | 2012-02-15 | 江西隆恒科技有限公司 | Oil-free double-screw compressor |
DE102012009103A1 (en) * | 2012-05-08 | 2013-11-14 | Ralf Steffens | spindle compressor |
JP6184837B2 (en) * | 2013-10-30 | 2017-08-23 | 株式会社日立産機システム | Screw compressor |
CA2972636C (en) * | 2015-01-15 | 2020-07-14 | Atlas Copco Airpower, Naamloze Vennootschap | Oil-injected vacuum pump element |
CN112780551A (en) * | 2021-02-26 | 2021-05-11 | 珠海格力电器股份有限公司 | Rotor subassembly, compressor and air conditioner |
CN116255335A (en) * | 2023-03-27 | 2023-06-13 | 英格索兰技术研发(上海)有限公司 | Vacuum pump |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080080997A1 (en) * | 2006-09-28 | 2008-04-03 | Kohtaro Chiba | Screw Compressor |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB282752A (en) | 1926-12-30 | 1928-05-31 | Josef Kozousek | Improvements in rotary machines for compressing and conveying liquids |
US2578196A (en) * | 1946-11-30 | 1951-12-11 | Imo Industri Ab | Screw compressor |
US3622256A (en) | 1969-10-14 | 1971-11-23 | Alexandr Ivanovich Borisoglebs | Screw-rotor machine |
JPS58131388A (en) * | 1982-01-29 | 1983-08-05 | Hitachi Ltd | Screw compressor |
US4560333A (en) * | 1984-02-07 | 1985-12-24 | Hitachi, Ltd. | Screw compressor |
JPH06100188B2 (en) * | 1984-09-05 | 1994-12-12 | 株式会社日立製作所 | Oil-free screw vacuum pump |
JPS6336083A (en) * | 1986-07-29 | 1988-02-16 | Mayekawa Mfg Co Ltd | Pressure alleviating device for delivery port of screw type compressor |
JPS6345488A (en) | 1986-08-11 | 1988-02-26 | Kobe Steel Ltd | Oil-free screw compressor |
JP2550066Y2 (en) * | 1990-08-28 | 1997-10-08 | 本田技研工業株式会社 | Screw compressor |
JPH04252887A (en) * | 1991-01-24 | 1992-09-08 | Hitachi Ltd | Oil-free screw compressor system |
JPH05302582A (en) * | 1992-04-24 | 1993-11-16 | Hitachi Ltd | Lubrication type screw compressor |
JPH05312174A (en) * | 1992-05-11 | 1993-11-22 | Hitachi Ltd | Screw vacuum pump |
JPH07247990A (en) * | 1994-03-09 | 1995-09-26 | Ebara Corp | Screw fluid machine provided with flow dividing port |
JPH09291891A (en) * | 1996-04-26 | 1997-11-11 | Hitachi Ltd | Screw compressor |
JPH10213085A (en) * | 1997-01-28 | 1998-08-11 | Kobe Steel Ltd | Screw compressor and casing casting method therefor |
JP2002013494A (en) * | 2000-06-29 | 2002-01-18 | Tochigi Fuji Ind Co Ltd | Fluid machine |
JP2008297944A (en) * | 2007-05-30 | 2008-12-11 | Hitachi Industrial Equipment Systems Co Ltd | Screw compressor |
-
2009
- 2009-05-28 JP JP2009129389A patent/JP5422260B2/en active Active
-
2010
- 2010-05-19 CN CN2010101855418A patent/CN101900119B/en active Active
- 2010-05-27 EP EP10164131.4A patent/EP2264319B1/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080080997A1 (en) * | 2006-09-28 | 2008-04-03 | Kohtaro Chiba | Screw Compressor |
Also Published As
Publication number | Publication date |
---|---|
CN101900119A (en) | 2010-12-01 |
JP2010275931A (en) | 2010-12-09 |
CN101900119B (en) | 2013-10-30 |
EP2264319A2 (en) | 2010-12-22 |
EP2264319A3 (en) | 2014-05-21 |
JP5422260B2 (en) | 2014-02-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2264319B1 (en) | Oil free screw compressor | |
KR101074633B1 (en) | The water cooling dry vacuum pump which has two phase screw type | |
EP1750011A1 (en) | Screw rotor and screw type fluid machine | |
EP3091231B1 (en) | Open type compressor | |
US8978824B2 (en) | Turbomachinery with integrated pump | |
JP6616891B2 (en) | Oil-cooled screw compressor | |
US11773853B2 (en) | Multi-stage screw compressor | |
US9121406B2 (en) | Scroll compressor and method for machining discharge port of the same | |
JP6053349B2 (en) | Scroll compressor | |
US9714572B2 (en) | Reduced noise screw machines | |
KR20160144948A (en) | Gerotor Pump with double rotor assembly | |
JP7356044B2 (en) | Screw compressor and refrigeration equipment | |
JP6427430B2 (en) | Screw compressor | |
KR20230150940A (en) | Rotor assemblies, compressors and air conditioners | |
US11415134B2 (en) | Screw rotor, fluid machine main body, and fluid machine | |
JP4248055B2 (en) | Oil-cooled screw compressor | |
CN112746970A (en) | Oil sump oil return structure, compressor and air conditioner | |
JP4321206B2 (en) | Gas compression device | |
JP3403452B2 (en) | Oilless screw compressor | |
WO2013156789A2 (en) | Screw machine with variable diameter rotors | |
JP2021102960A (en) | Screw type vacuum pump | |
JP2022069105A (en) | Screw compressor and screw rotor | |
JP2007263121A (en) | Evacuating apparatus | |
KR20160089590A (en) | Gerotor Pump with double rotor assembly | |
KR20170010406A (en) | Open-type 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 |
|
17P | Request for examination filed |
Effective date: 20100826 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME RS |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: TSURU, SEJI Inventor name: SAITO, TAKASHI Inventor name: UCHIDA, TOSHIKAZU |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: UCHIDA, TOSHIKAZU Inventor name: SAITO, TAKASHI Inventor name: TSURU, SEJI |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: UCHIDA, TOSHIKAZU Inventor name: TSURU, SEIJI Inventor name: SAITO, TAKASHI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: HITACHI, LTD. |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME RS |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04C 29/12 20060101ALI20140411BHEP Ipc: F04C 18/16 20060101AFI20140411BHEP Ipc: F04C 18/08 20060101ALI20140411BHEP Ipc: F04C 29/00 20060101ALI20140411BHEP Ipc: F04C 29/06 20060101ALI20140411BHEP |
|
TPAC | Observations filed by third parties |
Free format text: ORIGINAL CODE: EPIDOSNTIPA |
|
17Q | First examination report despatched |
Effective date: 20150529 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20160622 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: HITACHI, LTD. |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 861566 Country of ref document: AT Kind code of ref document: T Effective date: 20170115 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602010039457 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 861566 Country of ref document: AT Kind code of ref document: T Effective date: 20170111 |
|
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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170411 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170412 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170511 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170411 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170511 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602010039457 Country of ref document: DE |
|
RAP2 | Party data changed (patent owner data changed or rights of a patent transferred) |
Owner name: HITACHI INDUSTRIAL EQUIPMENT SYSTEMS CO., LTD. |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
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 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602010039457 Country of ref document: DE |
|
26N | No opposition filed |
Effective date: 20171012 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170527 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: PD Owner name: HITACHI INDUSTRIAL EQUIPMENT SYSTEMS CO., LTD.; JP Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), AFFECTATION / CESSION; FORMER OWNER NAME: HITACHI, LTD. Effective date: 20171012 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180131 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170527 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171201 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170527 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170527 |
|
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: 20170531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170527 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20100527 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170111 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20230418 Year of fee payment: 14 |