US20120195784A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- US20120195784A1 US20120195784A1 US13/501,181 US201013501181A US2012195784A1 US 20120195784 A1 US20120195784 A1 US 20120195784A1 US 201013501181 A US201013501181 A US 201013501181A US 2012195784 A1 US2012195784 A1 US 2012195784A1
- Authority
- US
- United States
- Prior art keywords
- suction
- valve
- valve plate
- pressure chamber
- gap
- 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.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
Abstract
A compressor includes a front housing having a crank chamber therein, a cylinder block having a cylinder bore therein, a rear housing including a low-pressure chamber and a high-pressure chamber therein, a valve plate on which a suction hole for communicating the cylinder bore and the low-pressure chamber is formed, and a suction valve disk for opening and closing the suction hole. A predetermined gap width is provided between the suction valve disk and an opening edge of the suction hole, and the gap width is set to 13-15% of a thickness of the suction valve disk. By the compressor, fixation of the suction valve on the valve plate is prevented. Therefore, noise-and-vibration performance improves and thereby generation of undesired noises is prevented. Further, since the fixation of the suction valve on the valve plate is prevented, a desired volume of refrigerant is surely supplied into the cylinder bore.
Description
- The present invention relates to a compressor, especially, to a compressor that has a suction valve for opening and closing a suction hole of a valve plate.
- In a Patent Document 1 listed below, a swash plate type variable capacity compressor is disclosed. In this swash plate type variable capacity compressor, a valve plate is provided between a cylinder block on which plural cylinder bores are formed and a rear housing in which a high-pressure chamber and a low-pressure chamber are formed. On the valve plate, formed are suction holes for communicating the cylinder bores with the low-pressure chamber. On a cylinder bore side of each suction holes, provided is a suction valve for opening and closing the suction hole. In addition, on the valve plate, formed are discharge holes for communicating the cylinder bores with the high-pressure chamber. On a high-pressure chamber side of each discharge hole, provided is a discharge valve for opening and closing the discharge hole.
- Then, the suction valves are bent toward the cylinder bores due to a suctioning operation of pistons to open the suction holes, so that refrigerant is suctioned from the low-pressure chamber to the cylinder bores. In addition, the discharge valves are bent toward the high-pressure chamber due to a discharging operation of the pistons to open the discharge holes, so that high-pressure refrigerant in the cylinder bores is discharged to the high-pressure chamber.
- A stroke displacement of the pistons changes according to a tilting angle of a swash plate, so that a capacity of refrigerant to be compressed changes. In addition, due to a rotation of the swash plate, suctioning refrigerant into the cylinder bores and compressing the refrigerant in the cylinder bores are sequentially done, and then the high-pressure refrigerant is discharged to the high-pressure chamber.
- In the above-explained conventional variable capacity compressor, lubrication oil is mixed in refrigerant to keep lubricity within the compressor. Therefore, the lubrication oil infiltrates between an opening edge portion of the suction hole on the valve plate and the suction valve, so that it is concerned that the suction valve may be fixed on the valve plate. In this case, a desired volume of refrigerant cannot be suctioned into the cylinder bores upon suctioning. In addition, if the suction valve that had been fixed on the valve plate suddenly separates from the valve plate, noises may be generated.
- Therefore, in a
Patent Document 2, disclosed is a compressor in which suction valves are prevented from fixing on a valve plate by providing gaps between the suction valves and the valve plate. - However, in this compressor, since the gaps are provided between the suction valves and the valve plate, a use of extra parts or a complicated working process is needed and thereby its production cost may increase.
-
- Patent Document 1: Japanese Patent Application Laid-Open No. H7-103138
- Patent Document 2: Japanese Patent Application Laid-Open No. 2005-42695
- An object of the present invention is to provide a compressor that can supply a desired volume of refrigerant into a cylinder bore without a fixation of a suction vale on a valve plate and can be easily produced.
- An aspect of the present invention provides a compressor that includes a front housing that has a crank chamber therein; a cylinder block that is fixed with the front housing and has a cylinder bore therein; a rear housing that is fixed with the cylinder block with interposing a valve plate therebetween and includes a low-pressure chamber and a high-pressure chamber therein; the valve plate that is provided between the cylinder block and the rear housing and on which a suction hole for communicating the cylinder bore and the low-pressure chamber is formed; and a suction valve disk that is attached on a side of the valve plate facing to the cylinder block and has a suction valve for opening and closing the suction hole, wherein a gap with a predetermined width is provided between the suction valve disk and an opening edge portion of the suction hole, and the width of the gap is set to 13 to 15% of a thickness of the suction valve disk.
- According to the aspect, the gap is provided between the opening edge portion of the suction hole and the suction valve and the width of the gap is set to 13 to 15% of the thickness of the suction valve disk, so that a fixation of the suction valve on the valve plate can be prevented. Therefore, noise-and-vibration performance can improve and thereby generation of undesired noises can be prevented. In addition, since the fixation of the suction valve on the valve plate can be prevented, a desired volume of refrigerant can be surely supplied into the cylinder bore.
- Note that it is preferable that the width of the gap is 0.065 to 0.175 mm when it is presented not as a relative value to the thickness of the suction valve disk but as an absolute value. According to this, the above-explained advantages can be achieved.
- Here, it is preferable that a groove is provided outside the opening edge portion. According to this, the fixation of the suction valve on the valve plate can be further prevented by introducing refrigerant gas into the groove.
- Further here, it is preferable that the gap is formed by a press working. According to this, it can be easily produced without using extra parts and can reduce a production cost.
-
FIG. 1 is an overall cross-sectional view of a compressor according to an embodiment. -
FIG. 2 is an enlarged cross-sectional view showing a valve plate, suction valves and discharge valves in the embodiment. -
FIG. 3 is a plan view of the valve plate and the suction valves. -
FIG. 4 (a) is a plan view of the valve plate, and (b) is an enlarged cross-sectional view taken along a line IVB-IVB shown in (a). -
FIG. 5 is an enlarged cross-sectional view of the valve plate and the suction valve. -
FIG. 6 is a graph chart showing noise-and-vibration performance and compression performance with respect to a gap width between the suction valve and an opening edge portion on the valve plate. - Hereinafter, an embodiment will be explained with reference to the drawings. As shown in
FIG. 1 , acompressor 100 includes a housing 1, avalve plate 5 and asuction valve disk 12. Thevalve plate 5 is assembled in the housing 1. Thesuction valve disk 12 includessuction valves 11 for opening and closingsuction holes 10 that communicate with a low-pressure chamber 8. Thesuction holes 10 are provided closer to a center of thevalve plate 5, anddischarge holes 16 are provided closer to an outer circumference of the valve plate 5 (seeFIG. 5 ). - The housing 1 is comprised of a
front housing 2, acylinder block 3 and arear housing 4. Acrank chamber 6 is formed in thefront housing 2. Thecylinder block 3 is fixed with thefront housing 2.Plural cylinder bores 7 are arranged in thecylinder block 3. Therear housing 4 is fixed with thecylinder block 3, and includes the low-pressure chamber 8 for suctioning refrigerant and a high-pressure chamber 9 for discharging compressed refrigerant. - The six
cylinder bores 7 are formed in thecylinder block 3 along its circumferential direction. Theplural cylinder bores 6 are formed about adrive shaft 30 at even intervals.Pistons 31 each of which is reciprocated are accommodated in thecylinder bores 7, respectively. Thepistons 31 are coupled with aswash plate 32 that rotates in thecrank chamber 6. - In the
rear housing 4, formed are the low-pressure chamber 8 and the high-pressure chamber 9 for refrigerant gas. The low-pressure chamber 8 is connected to an outlet side of a not-shown evaporator on a refrigeration cycle. The high-pressure chamber 9 is connected to an inlet side of a not-shown condenser on the refrigeration cycle. In addition, thevalve plate 5 is provided between thecylinder bores 7 and therear housing 4. - The
suction holes 10 are formed closer to the center on thevalve plate 5 with associated with the sixcylinder bores 7, and thesuction holes 16 are formed closer to the outer circumference. As explained above, thesuction holes 10 is opened and closed by thesuction valves 11, and thedischarge holes 11 are opened and closed by thedischarge valves 17. - At an end of the
front housing 2 that is not a connection end with thecylinder block 3, adrive mechanism 33 is rotatably supported. In thedrive mechanism 33, apulley 34 that receives a drive force from a not-shown engine is supported via abearing 35, and an end of thedrive shaft 30 is rotatably supported. Thepulley 34 and thedrive shaft 30 are engaged and disengaged by a magnetic clutch. - In a
compression mechanism 36, thedrive shaft 30 is provides so as to penetrate the crankchamber 6. As explained above, thedrive shaft 30 is rotated by receiving the drive force from thepulley 34. - A
lug plate 37 is provided in thecrank chamber 6, and integrally fixed with thedrive shaft 30. Ajournal 39 to which theswash plate 32 is fixed is attached to thedrive shaft 30. Thelug plate 37 and thejournal 39 are coupled with each other via alink mechanism 38. Due to a rotation of thedrive shaft 30, thelug plate 37 transfers the drive force to thejournal 39 through thelink mechanism 38. Thepistons 31 are coupled to a circumference of theswash plate 32 that is fixed with thejournal 39, and thepistons 32 reciprocate due to the rotation of thedrive shaft 30. Refrigerant is compressed by the reciprocation of thepistons 31. - Next, the
valve plate 5 and thesuction valve disk 12 will be explained in detail with reference toFIGS. 2 to 6 . - As shown in
FIG. 5( a), thevalve plate 5 is a circular plate, and the sixdischarge holes 16 are formed closer to its outer circumference at even intervals along its circumferential direction. These discharge holes 16 communicate the six cylinder bores 7 in thecylinder block 3 with the high-pressure chamber 9 in therear housing 4. In addition, the sixsuction holes 10 are formed, on an inward side of the six discharge holes 16, at even intervals along its circumferential direction. These suction holes 10 communicate the six cylinder bores 7 in thecylinder block 3 with the low-pressure chamber 8 in therear housing 4. - In addition, as shown in
FIG. 2 , thesuction valve disk 12 is provided on one side of thevalve plate 5 facing to thecylinder block 3, and adischarge valve disk 22 is provided on another side of thevalve plate 5 facing to therear housing 4. Thesuction valve disk 12 opens the suction hole(s) 10 when suctioning refrigerant into the cylinder bore(s) 7, and closes the suction hole(s) 10 when compressing refrigerant in the cylinder bore(s) 7. In addition, thedischarge valve disk 22 opens the discharge hole(s) 16 when compressing refrigerant in the cylinder bore(s) 7, and closes the discharge hole(s) 16 when suctioning refrigerant into the cylinder bore(s) 7. - As shown in
FIG. 3 , thesuction valve disk 12 is constituted by a circular thin plate-shapeddisk base 15, thesuction valves 11 provided along a circumferential direction of thedisk base 15 at even intervals, and communication holes 19 that are communicated with the discharge holes 16 on thevalve plate 5. Thesuction valve 10 is comprised of avalve body 18 provided at an inward of aU-shaped slit 20 and a pair of bridgingportions 21 that connects thevalve body 18 with thedisk base 15 between thecommunication hole 19 and theslit 20. - As shown in
FIG. 5 , agap 14 having a predetermined width is formed between thesuction valve disk 12 and anopening edge portion 23 of thesuction hole 10. The width S of thisgap 14 is set to 13 to 15% of a thickness t of thesuction valve disk 12. Thegap 14 is formed by reducing a thickness of the openingedge portion 23 smaller than that of abase portion 5 a of thevalve plate 5. In addition, thegap 14 is set within a range of the predetermined width 0.065 to 0.175 mm. - In addition, as shown in
FIGS. 2 and 4 , agroove 13 surrounding thesuction hole 10 is formed around thesuction hole 10. The openingedge portion 23 is formed between thegroove 13 and thesuction hole 10. A thickness of thevalve plate 5 associated with thegroove 13 is smaller than the thickness of the openingedge portion 23. - The predetermined width 0.065 to 0.175 mm of the
gap 14 will be explained with reference to a graph chart shown inFIG. 6 .FIG. 6 shows measurement results under a representative condition about noise-and-vibration performance and compressor performance with respect to the width S of thegap 14. Its horizontal axis refers to the width S of thegap 14, its vertical right axis refers to noise-and-vibration performance as pulsation (ΔPs), and its vertical left axis refers to compressor performance (Gr). A line A indicates a criterion for noise-and-vibration performance, and a line B indicates a criterion for compressor performance. In addition, a line C indicates a measurement result of noise-and-vibration performance of thesuction valve 11, and a line D indicates a measurement result of compressor performance. - A portion of the line C beyond the noise-and-vibration performance criterion A doesn't meet the performance criterion, so that generated noises and vibrations may become problems. In addition, a portion of the line C below the noise-and-vibration performance criterion A meets the performance criterion, so that generated noises and vibrations may not become problems. Therefore, where the line C runs above the noise-and-vibration performance criterion A, i.e. when the width S is less than 0.065 mm, the noise-and-vibration performance may have problems. But, when the width S is not less than 0.065 mm, the noise-and-vibration performance may not have problems. As a result, a minimum value for the width S of the
gap 14 is determined, so that the minimum width S of thegap 14 between thesuction valve 11 and theopening edge portion 23 is set to 0.065 mm. - Meanwhile, a portion of the line D located beyond the compressor performance criterion B meets the performance criterion, so that a desired volume of refrigerant can be supplied into the cylinder bores 7. In addition, a portion of the line D below the compressor performance criterion B doesn't meet the performance criterion, so that the desired volume of refrigerant cannot be supplied into the cylinder bores 7. Therefore, where the line C runs under the compressor performance criterion B, i.e. when the width S is more than 0.175 mm, the compressor performance may have problems. But, when the width S is not more than 0.175 mm, the compressor performance may not have problems. As a result, a maximum value for the width S of the
gap 14 is determined, so that the maximum width S of thegap 14 between thesuction valve 11 and theopening edge portion 23 is set to 0.175 mm. - Therefore, the predetermined width S of the
gap 14 is set within a range of 0.065 to 0.175 mm, the noise-and-vibration performance and the compressor performance can be met and the fixation of thesuction valves 11 on thevalve plate 5 can be prevented. - Next, explained will be a case where the predetermined width S of the
gap 14 is presented by a ratio to a thickness t of the valve plate 5 (13 to 15% in the present embodiment). - The range of the predetermined width S of the
gap 14 is set in the range within 0.065 to 0.175 mm as explained above. A minimum value of the thickness t of the valve plate 5 (i.e. a minimum thickness required for functioning as the valve plate 5) is generally 0.3 mm. In addition, a maximum value of the thickness t of the valve plate 5 (i.e. a maximum thickness capable of being installed in a compressor) is considered 0.5 mm as a common sense. Therefore, a ratio (S/t) of the minimum value 0.065 mm of the predetermined width S to the maximum value 0.5 mm of the thickness t is about 13%. In addition, a ratio (S/t) of the maximum value 0.175 mm of the predetermined width S to the minimum value 0.3 mm of the thickness t is about 50%. - As a result, the width S of this
gap 14 between thesuction valve disk 12 and theopening edge portion 23 of thesuction hole 10 on thevalve plate 5 is set to 13 to 15% of the thickness t of thesuction valve disk 12. - Next, operations of the compressor according to the present embodiment will be explained (see
FIG. 1 ). - In a state where the
piston 31 doesn't reciprocate in the cylinder bore 7 (i.e. a state where a suction/discharge operation is not done: a state where the piston is positions at its TDC or BDC or a state where theswash plate 32 is not substantively tilted), thesuction hole 10 is closed by thesuction valve 11 on the side ofvalve plate 5 facing to thecylinder block 3. Mean while, thedischarge hole 16 is closed by thedischarge valve 17 on the other side facing to therear housing 4. - When the
piston 31 starts its compression process in the cylinder bore 7 from the above state, compressed high-pressure refrigerant elastically bends thedischarge valve 17 to open thedischarge hole 16, and then is discharged from the cylinder bore 7 to the high-pressure chamber 9. When the compression of refrigerant finishes, thedischarge valve 17 reverts back to its normal shape to close thedischarge hole 16. Subsequently, when thepiston 31 starts its suction process in the cylinder bore 7, to-be-suctioned low-pressure refrigerant elastically bends the bridgingportions 21 of thesuction valve 11 to open thesuction hole 10, and then is suctioned from the low-pressure chamber 8 to thecylinder bore 7. - According to the present embodiment, the
gap 14 is provided between the openingedge portion 23 of thesuction hole 10 and thesuction valve 11 and thegap 14 is set with the range of 13 to 15% of the thickness of the suction valve disk 12 (0.065 to 0.175 mm), so that the fixation of thesuction valve 11 on thevalve plate 5 can be prevented. Therefore, noise-and-vibration performance can improve and thereby generation of undesired noises can be prevented. In addition, since the fixation of thesuction valve 11 on thevalve plate 5 can be prevented, the desired volume of refrigerant can be surely supplied into the cylinder bores 7. - In addition, since the
groove 13 is provided outside the openingedge portion 23, the fixation of thesuction valve 11 on thevalve plate 5 can be further prevented by introducing refrigerant gas into thegroove 13. - Further, since the
gap 14 is formed by a press working, it can be easily produced without using extra parts and can reduce a production cost. In this case, since thegroove 13 can become a space for receiving an extruded volume upon forming thegap 14 by a press working, the extruded volume can be prevented from heaving on a valve seat surface by forming thegroove 13. - Note that, the
groove 13 is provided on the side of thevalve plate 5 facing to thesuction valve 11 and thegap 14 is provided at theopening edge portion 23 between thesuction hole 10 and thegroove 13, as explained above. Similarly, an opening edge portion and a groove may be provided on the other side of thevalve plate 5 facing to the discharge valve 17 (seeFIG. 2 ). - In addition, the six cylinder bores 7 are formed in the
cylinder block 3 in the present embodiment, the number of them may not be six. The number of the cylinder bores 7 may be five, seven or the other.
Claims (4)
1. A compressor comprising:
a front housing that has a crank chamber therein;
a cylinder block that is fixed with the front housing and has a cylinder bore therein;
a rear housing that is fixed with the cylinder block with interposing a valve plate therebetween and includes a low-pressure chamber and a high-pressure chamber therein;
the valve plate that is provided between the cylinder block and the rear housing and on which a suction hole for communicating the cylinder bore and the low-pressure chamber is formed; and
a suction valve disk that is attached on a side of the valve plate facing to the cylinder block and has a suction valve for opening and closing the suction hole, wherein
a gap with a predetermined width is provided between the suction valve disk and an opening edge portion of the suction hole, and
the width of the gap is set to 13 to 15% of a thickness of the suction valve disk.
2. The compressor according to claim 1 , wherein the width of the gap is 0.065 to 0.175 mm.
3. The compressor according to claim 1 , wherein a groove is provided outside the opening edge portion.
4. The compressor according to claim 1 , wherein
the gap is formed by a press working.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009236498A JP2011085029A (en) | 2009-10-13 | 2009-10-13 | Compressor |
JP2009-236498 | 2009-10-13 | ||
PCT/JP2010/067854 WO2011046106A1 (en) | 2009-10-13 | 2010-10-12 | Compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20120195784A1 true US20120195784A1 (en) | 2012-08-02 |
Family
ID=43876156
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/501,181 Abandoned US20120195784A1 (en) | 2009-10-13 | 2010-10-12 | Compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20120195784A1 (en) |
EP (1) | EP2489877A1 (en) |
JP (1) | JP2011085029A (en) |
CN (1) | CN102575663A (en) |
WO (1) | WO2011046106A1 (en) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5603611A (en) * | 1995-03-22 | 1997-02-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston type compressor with simple but vibration-reducing suction reed valve mechanism |
US6382939B2 (en) * | 2000-01-17 | 2002-05-07 | Sanden Corporation | Reciprocating compressor in which a suction valve is previously bent to open a suction port when the compressor is stopped |
US6565336B1 (en) * | 1998-05-06 | 2003-05-20 | Carrier Corporation | Normally unseated suction valve |
US6675475B2 (en) * | 2001-05-10 | 2004-01-13 | Kabushiki Kaisha Toyota Jidoshokki | Method of producing shoe for swash plate type compressor |
US20060280617A1 (en) * | 2003-09-30 | 2006-12-14 | Katsumi Uehara | Compressor and suction valve structure |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES1000848Y (en) * | 1986-10-23 | 1988-11-01 | Goenaga Churruca Jose Maria | PERFECTED SUCTION VALVE DEVICE FOR AIR COMPRESSORS |
BR9002967A (en) * | 1990-06-19 | 1991-12-24 | Brasil Compressores Sa | VALVE FOR HERMETIC COOLING COMPRESSOR |
JP3326909B2 (en) | 1993-10-07 | 2002-09-24 | 株式会社豊田自動織機 | Swash plate type variable displacement compressor |
JP2005042695A (en) * | 2003-07-07 | 2005-02-17 | Calsonic Kansei Corp | Valve structure of compressor |
JP4395400B2 (en) * | 2004-03-31 | 2010-01-06 | カルソニックカンセイ株式会社 | Compressor valve structure |
JP2008031857A (en) * | 2006-07-26 | 2008-02-14 | Calsonic Kansei Corp | Compressor |
JP2008095522A (en) * | 2006-10-06 | 2008-04-24 | Sanden Corp | Suction valve mechanism |
-
2009
- 2009-10-13 JP JP2009236498A patent/JP2011085029A/en active Pending
-
2010
- 2010-10-12 WO PCT/JP2010/067854 patent/WO2011046106A1/en active Application Filing
- 2010-10-12 US US13/501,181 patent/US20120195784A1/en not_active Abandoned
- 2010-10-12 EP EP10823374A patent/EP2489877A1/en not_active Withdrawn
- 2010-10-12 CN CN2010800457089A patent/CN102575663A/en active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5603611A (en) * | 1995-03-22 | 1997-02-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston type compressor with simple but vibration-reducing suction reed valve mechanism |
US6565336B1 (en) * | 1998-05-06 | 2003-05-20 | Carrier Corporation | Normally unseated suction valve |
US6382939B2 (en) * | 2000-01-17 | 2002-05-07 | Sanden Corporation | Reciprocating compressor in which a suction valve is previously bent to open a suction port when the compressor is stopped |
US6675475B2 (en) * | 2001-05-10 | 2004-01-13 | Kabushiki Kaisha Toyota Jidoshokki | Method of producing shoe for swash plate type compressor |
US20060280617A1 (en) * | 2003-09-30 | 2006-12-14 | Katsumi Uehara | Compressor and suction valve structure |
Also Published As
Publication number | Publication date |
---|---|
CN102575663A (en) | 2012-07-11 |
JP2011085029A (en) | 2011-04-28 |
EP2489877A1 (en) | 2012-08-22 |
WO2011046106A1 (en) | 2011-04-21 |
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Legal Events
Date | Code | Title | Description |
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AS | Assignment |
Owner name: CALSONIC KANSEI CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:USUI, KEIGO;ISE, YUSUKE;REEL/FRAME:028026/0118 Effective date: 20120326 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |