US20020041812A1 - Seal structure for compressor - Google Patents
Seal structure for compressor Download PDFInfo
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- US20020041812A1 US20020041812A1 US09/971,479 US97147901A US2002041812A1 US 20020041812 A1 US20020041812 A1 US 20020041812A1 US 97147901 A US97147901 A US 97147901A US 2002041812 A1 US2002041812 A1 US 2002041812A1
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- Prior art keywords
- seal
- contacting portion
- protrusion
- shape
- annular
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0818—Flat gaskets
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- 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
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
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- 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
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0818—Flat gaskets
- F16J2015/0856—Flat gaskets with a non-metallic coating or strip
Definitions
- the present invention relates to a seal for a compressor.
- the compressor has an annular seal member that is placed between an annular portion of a first member and an annular portion of a second member.
- the compressor has a plurality of constituent housings in a housing assembly.
- the constituent housings are secured to each other.
- An annular seal member is placed between the constituent housings.
- the seal member prevents refrigerant in the housing assembly from leaking through between the constituent housings.
- Japanese Unexamined Patent Publication No. 8-261150, No. 9-42156, No. 11-125182 disclose a multiple seal structure.
- the multiple seal structure has multiple annular seal members. When a plurality of the seal members is used, the seal structure effectively prevents the refrigerant in a housing assembly from leaking through between constituent housings.
- the housing assembly increases thickness of its wall. As the thickness of the housing assembly increases, a configuration of the compressor becomes larger and heavier.
- the object of the present invention is to offer a single seal member that is placed on an annular portion between a first member and a second member so as to create a seal between the first member and the second member closely.
- a seal structure used in a compressor has a first member, a second member and a seal member with rigidity.
- the first member has a surface in a first shape.
- the first shape has at least a first contacting portion.
- the second member has a surface in a second shape.
- the second shape has at least a second contacting portion.
- the first shape and the second shape are complementary with each other.
- the seal member has a first seal surface and a second seal surface.
- the seal member is located between the first contacting portion and the second contacting portion.
- the seal member has a sufficient area to cover at least the first contacting portion and the second contacting portion.
- the seal member is press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member.
- FIG. 1 is a diagram in a cross-sectional view illustrating a first embodiment of a compressor seal according to the present invention
- FIG. 1( a ) is a partial enlarged view of FIG. 1 illustrating the first preferred embodiment of the compressor seal according to the present invention
- FIG. 2 is a partial exploded perspective view illustrating the first preferred embodiment of the compressor seal according to the present invention
- FIG. 3( a ) is a partial enlarged exploded cross-sectional view illustrating the first preferred embodiment of the compressor seal according to the present invention
- FIG. 3( b ) is a partial enlarged cross-sectional view illustrating the first preferred embodiment of the compressor seal according to the present invention
- FIG. 4 is a partial cross-sectional view illustrating a second embodiment of the compressor seal according to the present invention.
- FIG. 4( a ) is a partial enlarged view of FIG. 4 illustrating the second preferred embodiment of the compressor seal according to the present invention
- FIG. 4( b ) is a partial enlarged exploded cross-sectional view illustrating the second preferred embodiment of the compressor seal according to the present invention
- FIG. 5 is a partial enlarged cross-sectional view illustrating a third embodiment of the compressor seal according to the present invention.
- FIG. 6 is a partial enlarged cross-sectional view illustrating a fourth embodiment of the compressor seal according to the present invention.
- FIG. 7 is a partial cross-sectional view illustrating a fifth embodiment of the compressor seal according to the present invention.
- FIG. 7( a ) is a partial enlarged exploded cross-sectional view illustrating the fifth preferred embodiment of the compressor seal according to the present invention.
- FIG. 7( b ) is a partial enlarged cross-sectional view illustrating the fifth preferred embodiment of the compressor seal according to the present invention.
- FIGS. 1 through 3 a first embodiment of the present invention is described with reference to FIGS. 1 through 3.
- the present invention is applied to a fixed displacement type of a swash plate compressor.
- carbon dioxide is used as refrigerant.
- a swash plate 11 is accommodated in a swash plate housing 12 .
- a cylinder block 13 is secured to the swash plate housing 12 .
- a chamber housing 14 is secured to the cylinder block 13 .
- a motor housing 15 is secured to the chamber housing 14 .
- the swash plate housing 12 , the cylinder block 13 , the chamber housing 14 and the motor housing 15 constitute a housing assembly 10 .
- the swash plate housing 12 , the cylinder block 13 , the chamber housing 14 and the motor housing 15 are fixed by securing together by bolts. The bolts are not illustrated in FIG. 1.
- the swash plate housing 12 and the cylinder block 13 are considered as a first housing and a second housing in the housing assembly 10 .
- the cylinder block 13 and the chamber housing 14 are also considered as a first housing and a second housing in the housing assembly 10 .
- the chamber housing 14 and the motor housing 15 are also optionally considered as a first housing and a second housing in the housing assembly 10 . Between the above first and second housings, one preferred embodiment of the compressor seal according to the present invention is placed.
- a drive shaft 16 is rotatably supported by radial bearings 17 and 18 in the swash plate housing 12 and the motor housing 15 .
- the drive shaft 16 extends through the cylinder block 13 and the chamber housing 14 .
- the swash plate 11 is mounted on the drive shat 16 in the swash plate housing 12 .
- a stator 19 is fixed to an inner circumferential surface of the motor housing 15 .
- a rotor 20 is mounted on the drive shaft 16 in the motor housing 15 .
- the stator 19 When the stator 19 is energized, the rotor 20 is rotated.
- the drive shaft 16 rotates integrally with the rotor 20 .
- multiple cylinder bores 131 are formed in the cylinder block 13 .
- the multiple cylinder bores 131 are arranged to surround the drive shaft 16 at equal intervals.
- a piston 21 is accommodated in each of the cylinder bores 131 .
- a pair of shoes 22 is placed between the swash plate 11 and the piston 21 . Rotational movement of the swash plate 11 is converted to reciprocal movement of the piston 21 in the cylinder bore 131 through the shoes 22 .
- a port plate 23 , a suction valve plate 24 , a discharge valve plate 25 and a retainer plate 26 are placed between the chamber housing 14 and the cylinder block 13 .
- the chamber housing 14 is parted into a suction chamber 142 and a discharge chamber 143 by a partition 141 .
- a suction port 231 is formed on the retainer plate 26 , the discharge valve plate 25 and the port plate 23 to correspond to the suction chamber 142 and each of the cylinder bores 131 .
- a discharge port 232 is formed on the discharge plate 24 and the port plate 23 to correspond to the discharge chamber 143 and each of the cylinder bores 131 .
- a suction valve 241 is formed on the suction valve plate 24 and a discharge valve 251 is formed on the discharge valve plate 25 . The suction valve 241 opens and closes the suction port 231 , and the discharge valve 251 opens and closes the discharge port 232 .
- the swash plate 11 has a boss 111 .
- the swash plate housing 12 has an end wall 121 .
- a thrust bearing 27 is placed between the boss 111 and the end wall 121 .
- compressive reaction force is generated.
- the end wall 121 receives the compressive reaction force through the piston 2 1 , the shoes 22 , the swash plate 11 and the thrust bearing 27 .
- the chamber housing 14 has an end wall 144 .
- An axial through hole 145 is formed at the end wall 144 to insert the drive shaft 16 .
- the refrigerant in the discharge chamber 143 flows into the motor housing 15 through the axial through hole 145 .
- a discharge passage 151 is formed in the motor housing 15 .
- the refrigerant in the motor housing 15 flows through the discharge passage 151 into an external refrigerant circuit which is not illustrated in FIG. 1.
- the external refrigerant circuit has a condenser, an expansion valve and an evaporator.
- a suction passage 146 is formed in the chamber housing 14 . The refrigerant is returned to the suction chamber 142 through the condenser, the expansion valve, the evaporator and the suction passage 146 .
- the motor housing 15 communicates with the discharge chamber 143 through the axial through hole 145 and maintains discharge pressure.
- the swash plate housing 12 communicates with the discharge chamber 143 through the axial through hole 132 formed in the cylinder block 13 and also maintains discharge pressure.
- the radial bearings 17 and 18 , the thrust bearing 27 as well as sliding portions between the swash plate 11 and the shoes 22 are all lubricated by lubricant oil which flows in carbon dioxide in the first embodiment.
- the swash plate housing 12 is a first member and the cylinder block 13 is a second member.
- An annular gasket 31 as a seal member is placed between an end surface 29 of a circumferential wall 28 of the swash plate housing 12 and an outer circumferential portion of an end surface 30 of the cylinder block 13 .
- the first member, the second member and the seal member have a closed shape surface such as an annular surface.
- the end surfaces 29 and 30 are respectively annular securing portions of the swash plate housing 12 and the cylinder block 13 .
- annular protrusion 39 in a substantially rectangular or square shape is formed on the end surface 29
- annular recess 40 in a substantially rectangular or square shape is formed on the outer circumferential portion in one preferred embodiment.
- the annular protrusion 39 and the annular recess 40 are complementary with each other.
- Height K 1 of the annular protrusion 39 is smaller than thickness T of the gasket 3 1 .
- Depth F 1 of the annular recess 40 is larger than the height K 1 of the annular protrusion 39 .
- a width H 2 of the annular recess 40 is larger than a width H 1 of the annular protrusion 39 .
- a diameter D 1 of an inner circumferential step 391 of the annular protrusion 39 is larger than a diameter D 2 of an inner circumferential step 401 of the annular recess 40 in one preferred embodiment.
- a diameter D 3 of an outer circumferential step 392 of the annular protrusion 39 is smaller than a diameter D 4 of an outer circumferential step 402 of the annular recess 40 .
- the step 391 of the protrusion 39 is positioned further away from the drive shaft 16 than the step 401 .
- the step 402 of the annular recess 40 is positioned further away from the drive shaft 16 than the step 392 to surround the step 392 with respect to the drive shaft 16 .
- the annular protrusion 39 has an inner protruding edge 393 and an outer protruding edge 394 with respect to the axis 161 which is shown in FIG. 1.
- the annular recess 40 forms an inner base edge 403 and an outer base edge 404 with respect to the axis 161 .
- a diameter of the inner protruding edge 393 or the diameter D 1 of the step 391 is larger than a diameter of the inner base edge 403 or the diameter D 2 of the step 401 .
- a diameter of an outer protruding edge 394 or the diameter D 3 of the step 392 is smaller than a diameter of an outer base edge 404 or the diameter D 4 of the step 402 .
- FIG. 3( a ) illustrates a state before the swash plate housing 12 and the cylinder block 13 are assembled.
- the gasket 31 includes a base plate 311 and seal layers 312 , 313 which are fixed to both surfaces of the base plate 311 .
- the base plate 311 is made of metal while the seal layers 312 and 313 are made of rubber.
- the gasket 31 is flat.
- FIG. 3( b ) the swash plate housing 12 and the cylinder block 13 are assembled to sandwich the gasket 31 .
- the gasket 31 is sandwiched and deformed by the annular protrusion 39 and the annular recess 40 .
- the gasket 31 has a first seal surface 314 and a second seal surface 315 .
- the protruding edges 393 and 394 are contacting portions of the first seal surface 314 .
- the base edges 403 and 404 are contacting portions of the second seal surface 315 .
- the inner protruding edge 393 is a first contacting portion that corresponds to the inner base edge 403 .
- the inner base edge 403 is a second contacting portion that corresponds to the inner protruding edge 393 .
- the outer protruding edge 394 is a first contacting portion that corresponds to the outer base edge 404 .
- the outer base edge 404 is a second contacting portion that corresponds to the outer protruding edge 394 .
- annular gasket 35 is placed between an outer circumferential portion of an end surface 32 of the cylinder block 13 and an end surface 34 of a circumferential wall 33 of the chamber housing 14 .
- annular gasket 38 is placed between an outer circumferential portion of an outer end surface 147 of the end wall 144 of the chamber housing 14 and an end surface 37 of a circumferential wall 36 of the motor housing 15 .
- the gaskets 35 and 38 are substantially similar to the gasket 31 and are placed in a substantially similar manner.
- the end surfaces 32 and 34 are respectively annular securing portions of the cylinder block 13 and the chamber housing 14 .
- the end surface 37 and the outer end surface 147 are respectively annular securing portions of the chamber housing 14 and the motor housing 15 .
- annular recess 41 is formed on the outer circumferential portion of the end surface 32 of the cylinder block 13 .
- An annular protrusion 42 is formed on the end surface 34 of the circumferential wall 33 of the chamber housing 14 .
- the annular protrusion 41 and the annular recess 42 are complementary with each other.
- An annular recess 43 is formed on the outer circumferential portion of the outer end surface 147 of the chamber housing 14 .
- An annular protrusion 44 is formed on the end surface 37 of the circumferential wall 36 of the motor housing 15 .
- the annular protrusion 43 and the annular recess 44 are complementary with each other.
- the annular protrusions 42 and 44 are in a substantially similar shape as the annular protrusion 39 .
- the annular recesses 41 and 43 are also in a substantially similar shape as the annular recess 40 .
- the annular protrusion 42 is received in the annular recess 41 while the annular protrusion 44 is received in the annular recess 43 .
- the end surface 29 and the end surface 30 approach with each other to have a distance which is nearly equal to the thickness T of the gasket 31 .
- the height K 1 of the annular protrusion 39 is smaller than the thickness T of the gasket 31 in one preferred embodiment. Therefore, the protruding edges 393 , 394 and the base edges 403 , 404 approach with each other to have intervals t which are smaller than the thickness T of the gasket 31 . Accordingly, as shown in FIGS. 3 ( a ) and 3 ( b ), the protruding edges 393 and 394 contact the first seal surface 314 of the seal layer 312 .
- the base edges 403 and 404 contact the second seal surface 315 of the seal layer 313 .
- the inner protruding edge 393 pushes the gasket 31 towards the end surface 30 outside the inner base edge 403 with respect to the axis 161 which is shown in FIG. 1, while the inner base edge 403 pushes the gasket 31 towards the end surface 29 inside the inner protruding edge 393 with respect to the axis 161 .
- the outer protruding edge 394 pushes the gasket 31 towards the end surface 30 inside the outer base edge 404 with respect to the axis 161 , while the outer base edge 404 pushes the gasket 31 towards the end surface 29 outside the outer protruding edge 394 with respect to the axis 161 .
- the annular gasket 31 is deformed in a direction of the thickness of the annular gasket 31 or in a direction of the annular protrusion. The deformation is made over all circumferences of the annular gasket 31 .
- the annular gasket 31 is deformed against rigidity of the base plate 311 over all circumferences of the annular gasket 31 .
- the protruding edges 393 , 394 press-contact the seal layer 312 and the base edges 403 , 404 press-contact the seal layer 313 .
- the protruding ends 393 , 394 and the base ends 403 , 404 are linear contacting portions and increase pressure against the seal layers 312 and 313 when press-contacted. Such high-pressure prevents refrigerant in the housing assembly 10 from leaking through between the gasket 31 and the end surface 29 as well as between the gasket 31 and the end surface 30 .
- Carbon dioxide is used in higher pressure than fluoro series. Carbon dioxide in the high-pressure permeates into a seal member made of rubber. When carbon dioxide decreases its pressure, carbon dioxide in the seal member expands to damage the seal member. This damage deteriorates function of the seal member.
- the gasket 31 is formed by affixing the seal layers 312 and 313 made of rubber to both surfaces of the base plate 311 . As thickness of the seal layers 312 and 313 is decreased, little carbon dioxide in high-pressure permeates into the seal layers 312 and 313 . For the above reason, foaming is substantially reduced. Accordingly, the seal layers 312 and 313 are not damaged.
- contacting portions increase pressure against the seal layers 312 and 313 .
- the above contacting portions are easily formed.
- the gasket 31 is flat. Therefore, both surfaces of the gasket 31 correspond to contact the end surface 29 or the end surface 30 .
- the seal layer 312 contacts the end surface 29 while the seal layer 312 contacts the end surface 30 .
- the seal layer 313 contacts the end surface 29 while the seal layer 313 contacts the end surface 30 . Accordingly, the gasket 31 is convenient to use.
- the annular gasket 31 has thickness that is much smaller than a diameter of the annular gasket 31 and is easily deformed equally over all circumferences of the annular gasket 31 .
- the annular gaskets 35 and 38 function in substantially the same way as the annular gasket 31 .
- the annular protrusions 42 and 44 function in substantially the same way as the annular protrusion 39 .
- the annular recesses 41 and 43 function in substantially the same way as the annular recess 40 .
- FIGS. 4 , 4 ( a ) and 4 ( b ) A second preferred embodiment of the present invention will be described with reference to FIGS. 4 , 4 ( a ) and 4 ( b ).
- the same reference numerals of the first preferred embodiment are applied to substantially the same components in the second preferred embodiment.
- An annular protrusion 45 is formed on the end surface 29 of the circumferential wall 28 of the swash plate housing 12 .
- An annular indentation 46 is formed on the outer circumferential portion of the end surface 30 of the cylinder block 13 .
- the annular protrusion 45 has a protrusion with a single step on the end surface 29 which is a securing portion.
- the indentation 46 forms a recess with a single step on the outer circumferential portion which is a securing portion.
- the annular protrusion 45 and the annular indentation 46 are complementary with each other.
- Height K 2 of the annular protrusion 45 is smaller than the thickness T of the gasket 31 .
- Depth F 2 of the annular indentation 46 is substantially equal to the height K 2 of the annular protrusion 45 .
- a width H 4 of the annular indentation 46 is larger than a width H 3 of the annular protrusion 45 .
- a diameter of the step 451 of the annular protrusion 45 is larger than a diameter of the step 461 of the annular indentation 46 .
- a third preferred embodiment of the present invention will be described with reference to FIG. 5.
- the same reference numerals of the first preferred embodiment are applied to substantially the same components of the third preferred embodiment.
- An annular protrusion 47 has a triangular shape with a pair of tapers 471 and 472 .
- the tapers 471 and 472 cross on a top 473 of the annular protrusion 47 which is a first contacting portion and press-contact the seal layer 312 of the annular gasket 31 .
- An annular recess 48 has a pair of tapers 481 and 482 .
- the tapers 481 and 482 respectively cross the end surface 30 on a pair of edge portions 483 and 484 , which are second contacting portions and press-contact the seal layer 313 of the annular gasket 31 .
- the annular protrusion 47 and the annular recess 48 are complementary with each other.
- a fourth preferred embodiment of the present invention will be described with reference to FIG. 6.
- the same reference numerals of the first preferred embodiment are applied to substantially the same components of the fourth preferred embodiment.
- An annular protrusion 49 has a convex or a semicircular shape in a radial cross section.
- An annular recess 50 forms a concave or a semicircular shape in the radial cross section.
- the annular protrusion 49 and the annular recess 50 are complementary with each other.
- a top 491 of the annular protrusion 49 is a first contacting portion and press-contacts the seal layer 312 of the annular gasket 31 .
- a partial circle of the annular recess 50 is formed on the end surface 30 between a pair of edge portions 501 and 502 , which are second contacting portions and press-contact the seal layer 313 of the annular gasket 31 .
- FIGS. 7 , 7 ( a ), 7 ( b ) A fifth preferred embodiment of the present invention will be described with reference to FIGS. 7 , 7 ( a ), 7 ( b ).
- the same reference numerals of the first preferred embodiment are applied to substantially the same components of the fifth preferred embodiment.
- the suction valve 241 is formed on a suction valve plate 24 A.
- the suction valve plate 24 A is also a gasket.
- the gasket 24 A includes a base plate 242 and seal layers 243 , 244 which are fixed to both surfaces of the base plate 242 .
- the base plate 242 is made of metal while the seal layers 243 , 244 are made of rubber.
- the annular recess 41 is formed on the cylinder block 13 .
- the annular recess 41 forms an inner base edge 413 with an inner step 411 and an outer base edge 414 with an outer step 412 with respect to the axis 161 which is shown in FIG. 1.
- the base edges 413 , 414 are second contacting portions which contact a second seal surface 246 of the suction valve plate 24 A.
- the annular protrusion 42 is formed on the chamber housing 14 .
- the annular protrusion has an inner protruding edge 423 with an inner step 421 and an outer protruding edge 424 with an outer step 422 with respect to the axis 161 .
- the protruding edges 423 , 424 are first contacting portions which contact a first seal surface 245 of the suction valve plate 24 A.
- the suction valve plate 24 A is flat. When the cylinder block 13 and the chamber housing 14 are assembled, an outer circumferential portion of the suction valve plate 24 A is deformed over all circumferences of the annular gasket 31 . In the above described preferred embodiment, since the suction valve plate 24 A is also used as a gasket, the number of parts is reduced.
- the present invention is applied to a variable displacement compressor which is disclosed in Japanese Unexamined Patent Publication No. 2000-170656.
- the variable displacement compressor has a control valve housing and a compressor housing.
- the present invention is applied to a seal between the control valve housing and the compressor housing using a gasket.
- the control valve housing is a first member and the compressor housing is a second member. The control valve housing and the compressor housing are secured to each other.
- the present invention is not applied only to a swash plate type compressor, but also to a scroll type compressor, a vane type compressor and other types of compressors.
- a seal structure used in a compressor has a first member, a second member and a seal member with rigidity.
- the first member has a surface in a first shape.
- the first shape has at least a first contacting portion.
- the second member has a surface in a second shape.
- the second shape has at least a second contacting portion.
- the first shape and the second shape are complementary with each other.
- the seal member has a first seal surface and a second seal surface.
- the seal member is located between the first contacting portion and the second contacting portion.
- the seal member has a sufficient area to cover at least the first contacting portion and the second contacting portion.
- the seal member is press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member. Accordingly, the single seal member is placed between an annular portion of the first member and a corresponding annular portion of the second member to closely seal the first member and the second member.
Abstract
A seal structure used in a compressor has a first member, a second member and a seal member with a rigidity. The first member has a surface in a first shape. The first shape has at least a first contacting portion. The second member has a surface in a second shape. The second shape has at least a second contacting portion. The first shape and the second shape are complementary with each other. The seal member has a first seal surface and a second seal surface. The seal member is located between the first contacting portion and the second contacting portion. The seal member has a sufficient area to cover at least the first contacting portion and the second contacting portion. The seal member is press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member.
Description
- The present invention relates to a seal for a compressor. The compressor has an annular seal member that is placed between an annular portion of a first member and an annular portion of a second member.
- The compressor has a plurality of constituent housings in a housing assembly. The constituent housings are secured to each other. An annular seal member is placed between the constituent housings. The seal member prevents refrigerant in the housing assembly from leaking through between the constituent housings. For example, Japanese Unexamined Patent Publication No. 8-261150, No. 9-42156, No. 11-125182 disclose a multiple seal structure. The multiple seal structure has multiple annular seal members. When a plurality of the seal members is used, the seal structure effectively prevents the refrigerant in a housing assembly from leaking through between constituent housings.
- In the multiple seal structure, however, due to various diameters of the multiple seal members the housing assembly increases thickness of its wall. As the thickness of the housing assembly increases, a configuration of the compressor becomes larger and heavier.
- As refrigerant carbon dioxide requires higher pressure than fluoro series. Carbon dioxide in the high-pressure permeates into a seal member made of rubber. When carbon dioxide decreases its pressure, carbon dioxide inside the seal member expands. This expansion or foaming damages the seal member. For the above reason, the seal member made of rubber is generally unsuitable for a compressor when carbon dioxide is used as refrigerant.
- The object of the present invention is to offer a single seal member that is placed on an annular portion between a first member and a second member so as to create a seal between the first member and the second member closely.
- To achieve the above object, the present invention has following features. A seal structure used in a compressor has a first member, a second member and a seal member with rigidity. The first member has a surface in a first shape. The first shape has at least a first contacting portion. The second member has a surface in a second shape. The second shape has at least a second contacting portion. The first shape and the second shape are complementary with each other. The seal member has a first seal surface and a second seal surface. The seal member is located between the first contacting portion and the second contacting portion. The seal member has a sufficient area to cover at least the first contacting portion and the second contacting portion. The seal member is press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member.
- The features of the present invention that are believed to be novel are set forth with particularity in the appended claims. The invention together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
- FIG. 1 is a diagram in a cross-sectional view illustrating a first embodiment of a compressor seal according to the present invention;
- FIG. 1(a) is a partial enlarged view of FIG. 1 illustrating the first preferred embodiment of the compressor seal according to the present invention;
- FIG. 2 is a partial exploded perspective view illustrating the first preferred embodiment of the compressor seal according to the present invention;
- FIG. 3(a) is a partial enlarged exploded cross-sectional view illustrating the first preferred embodiment of the compressor seal according to the present invention;
- FIG. 3(b) is a partial enlarged cross-sectional view illustrating the first preferred embodiment of the compressor seal according to the present invention;
- FIG. 4 is a partial cross-sectional view illustrating a second embodiment of the compressor seal according to the present invention;
- FIG. 4(a) is a partial enlarged view of FIG. 4 illustrating the second preferred embodiment of the compressor seal according to the present invention;
- FIG. 4(b) is a partial enlarged exploded cross-sectional view illustrating the second preferred embodiment of the compressor seal according to the present invention;
- FIG. 5 is a partial enlarged cross-sectional view illustrating a third embodiment of the compressor seal according to the present invention;
- FIG. 6 is a partial enlarged cross-sectional view illustrating a fourth embodiment of the compressor seal according to the present invention;
- FIG. 7 is a partial cross-sectional view illustrating a fifth embodiment of the compressor seal according to the present invention;
- FIG. 7(a) is a partial enlarged exploded cross-sectional view illustrating the fifth preferred embodiment of the compressor seal according to the present invention; and
- FIG. 7(b) is a partial enlarged cross-sectional view illustrating the fifth preferred embodiment of the compressor seal according to the present invention.
- Firstly, a first embodiment of the present invention is described with reference to FIGS. 1 through 3. The present invention is applied to a fixed displacement type of a swash plate compressor. In this embodiment, carbon dioxide is used as refrigerant.
- As shown in FIG. 1, a
swash plate 11 is accommodated in aswash plate housing 12. Acylinder block 13 is secured to theswash plate housing 12. Achamber housing 14 is secured to thecylinder block 13. Amotor housing 15 is secured to thechamber housing 14. The swash plate housing 12, thecylinder block 13, thechamber housing 14 and themotor housing 15 constitute ahousing assembly 10. The swash plate housing 12, thecylinder block 13, the chamber housing 14 and themotor housing 15 are fixed by securing together by bolts. The bolts are not illustrated in FIG. 1. Theswash plate housing 12 and thecylinder block 13 are considered as a first housing and a second housing in thehousing assembly 10. Similarly, thecylinder block 13 and thechamber housing 14 are also considered as a first housing and a second housing in thehousing assembly 10. The chamber housing 14 and themotor housing 15 are also optionally considered as a first housing and a second housing in thehousing assembly 10. Between the above first and second housings, one preferred embodiment of the compressor seal according to the present invention is placed. - A
drive shaft 16 is rotatably supported byradial bearings swash plate housing 12 and themotor housing 15. Thedrive shaft 16 extends through thecylinder block 13 and thechamber housing 14. Theswash plate 11 is mounted on thedrive shat 16 in theswash plate housing 12. - A
stator 19 is fixed to an inner circumferential surface of themotor housing 15. Arotor 20 is mounted on thedrive shaft 16 in themotor housing 15. When thestator 19 is energized, therotor 20 is rotated. Thedrive shaft 16 rotates integrally with therotor 20. - Still referring to FIG. 1, multiple cylinder bores131 are formed in the
cylinder block 13. In the first embodiment, as shown in FIG. 2, four cylinder bores are formed. The multiple cylinder bores 131 are arranged to surround thedrive shaft 16 at equal intervals. Apiston 21 is accommodated in each of the cylinder bores 131. A pair ofshoes 22 is placed between theswash plate 11 and thepiston 21. Rotational movement of theswash plate 11 is converted to reciprocal movement of thepiston 21 in the cylinder bore 131 through theshoes 22. - A
port plate 23, asuction valve plate 24, adischarge valve plate 25 and aretainer plate 26 are placed between thechamber housing 14 and thecylinder block 13. Thechamber housing 14 is parted into asuction chamber 142 and adischarge chamber 143 by apartition 141. - A
suction port 231 is formed on theretainer plate 26, thedischarge valve plate 25 and theport plate 23 to correspond to thesuction chamber 142 and each of the cylinder bores 131. Adischarge port 232 is formed on thedischarge plate 24 and theport plate 23 to correspond to thedischarge chamber 143 and each of the cylinder bores 131. Asuction valve 241 is formed on thesuction valve plate 24 and adischarge valve 251 is formed on thedischarge valve plate 25. Thesuction valve 241 opens and closes thesuction port 231, and thedischarge valve 251 opens and closes thedischarge port 232. - While the
piston 21 moves from a left side to a right side in FIG. 1, refrigerant in thesuction chamber 142 is drawn into the cylinder bore 131 as thesuction valve 241 is pushed away from thesuction port 231. While thepiston 21 moves from the right side to the left side in FIG. 1, the refrigerant in the cylinder bore 131 is discharged into thedischarge chamber 143 as thedischarge valve 251 is pushed away from thedischarge port 232. Aretainer 261 on theretainer plate 26 regulates an opening of thedischarge valve 251. - The
swash plate 11 has aboss 111. Theswash plate housing 12 has anend wall 121. Athrust bearing 27 is placed between theboss 111 and theend wall 121. As the refrigerant is discharged from the cylinder bore 131 into thedischarge chamber 143 by the reciprocal movement of thepiston 21, compressive reaction force is generated. At this time, theend wall 121 receives the compressive reaction force through the piston 2 1, theshoes 22, theswash plate 11 and thethrust bearing 27. - The
chamber housing 14 has anend wall 144. An axial throughhole 145 is formed at theend wall 144 to insert thedrive shaft 16. The refrigerant in thedischarge chamber 143 flows into themotor housing 15 through the axial throughhole 145. Adischarge passage 151 is formed in themotor housing 15. The refrigerant in themotor housing 15 flows through thedischarge passage 151 into an external refrigerant circuit which is not illustrated in FIG. 1. The external refrigerant circuit has a condenser, an expansion valve and an evaporator. Asuction passage 146 is formed in thechamber housing 14. The refrigerant is returned to thesuction chamber 142 through the condenser, the expansion valve, the evaporator and thesuction passage 146. Themotor housing 15 communicates with thedischarge chamber 143 through the axial throughhole 145 and maintains discharge pressure. Theswash plate housing 12 communicates with thedischarge chamber 143 through the axial throughhole 132 formed in thecylinder block 13 and also maintains discharge pressure. Theradial bearings swash plate 11 and theshoes 22 are all lubricated by lubricant oil which flows in carbon dioxide in the first embodiment. - As shown in FIG. 1(a), the
swash plate housing 12 is a first member and thecylinder block 13 is a second member. Anannular gasket 31 as a seal member is placed between anend surface 29 of acircumferential wall 28 of theswash plate housing 12 and an outer circumferential portion of anend surface 30 of thecylinder block 13. The first member, the second member and the seal member have a closed shape surface such as an annular surface. The end surfaces 29 and 30 are respectively annular securing portions of theswash plate housing 12 and thecylinder block 13. - As shown in FIGS.3(a) and 3(b), an
annular protrusion 39 in a substantially rectangular or square shape is formed on theend surface 29, and anannular recess 40 in a substantially rectangular or square shape is formed on the outer circumferential portion in one preferred embodiment. Theannular protrusion 39 and theannular recess 40 are complementary with each other. Height K1 of theannular protrusion 39 is smaller than thickness T of the gasket 3 1. Depth F1 of theannular recess 40 is larger than the height K1 of theannular protrusion 39. A width H2 of theannular recess 40 is larger than a width H1 of theannular protrusion 39. - As shown in FIG. 2, a diameter D1 of an inner
circumferential step 391 of theannular protrusion 39 is larger than a diameter D2 of an innercircumferential step 401 of theannular recess 40 in one preferred embodiment. A diameter D3 of an outercircumferential step 392 of theannular protrusion 39 is smaller than a diameter D4 of an outercircumferential step 402 of theannular recess 40. - Now referring back to FIGS. 1 and 1(a), as the compressor is seen in a cross-sectional view along a direction of an
axis 161 of thedrive shaft 16, thestep 391 of theprotrusion 39 is positioned further away from thedrive shaft 16 than thestep 401. In the same way, thestep 402 of theannular recess 40 is positioned further away from thedrive shaft 16 than thestep 392 to surround thestep 392 with respect to thedrive shaft 16. When the compressor is seen in a cross-sectional view along the direction of theaxis 161 of thedrive shaft 16, theannular protrusion 39 is received in theannular recess 40. - As shown in FIGS.3(a) and 3(b) and in combination with FIG. 2, the
annular protrusion 39 has an innerprotruding edge 393 and an outer protruding edge 394 with respect to theaxis 161 which is shown in FIG. 1. Theannular recess 40 forms aninner base edge 403 and anouter base edge 404 with respect to theaxis 161 . A diameter of the inner protrudingedge 393 or the diameter D1 of thestep 391 is larger than a diameter of theinner base edge 403 or the diameter D2 of thestep 401. A diameter of an outer protruding edge 394 or the diameter D3 of thestep 392 is smaller than a diameter of anouter base edge 404 or the diameter D4 of thestep 402. - FIG. 3(a) illustrates a state before the
swash plate housing 12 and thecylinder block 13 are assembled. Thegasket 31 includes abase plate 311 and seallayers base plate 311. Thebase plate 311 is made of metal while the seal layers 312 and 313 are made of rubber. Thegasket 31 is flat. - In FIG. 3(b), the
swash plate housing 12 and thecylinder block 13 are assembled to sandwich thegasket 31. Herein, thegasket 31 is sandwiched and deformed by theannular protrusion 39 and theannular recess 40. - Still referring to FIGS.3(a) and 3(b), the
gasket 31 has afirst seal surface 314 and asecond seal surface 315. The protruding edges 393 and 394 are contacting portions of thefirst seal surface 314. The base edges 403 and 404 are contacting portions of thesecond seal surface 315. The innerprotruding edge 393 is a first contacting portion that corresponds to theinner base edge 403. Theinner base edge 403 is a second contacting portion that corresponds to the inner protrudingedge 393. In the same way, the outer protruding edge 394 is a first contacting portion that corresponds to theouter base edge 404. Theouter base edge 404 is a second contacting portion that corresponds to the outer protruding edge 394. - Referring to FIG. 1, between an outer circumferential portion of an
end surface 32 of thecylinder block 13 and an end surface 34 of acircumferential wall 33 of thechamber housing 14, anannular gasket 35 is placed. Between an outer circumferential portion of anouter end surface 147 of theend wall 144 of thechamber housing 14 and an end surface 37 of acircumferential wall 36 of themotor housing 15, anannular gasket 38 is placed. In a preferred embodiment, thegaskets gasket 31 and are placed in a substantially similar manner. - The end surfaces32 and 34 are respectively annular securing portions of the
cylinder block 13 and thechamber housing 14. The end surface 37 and theouter end surface 147 are respectively annular securing portions of thechamber housing 14 and themotor housing 15. - Still referring to FIG. 1, an
annular recess 41 is formed on the outer circumferential portion of theend surface 32 of thecylinder block 13. Anannular protrusion 42 is formed on the end surface 34 of thecircumferential wall 33 of thechamber housing 14. Theannular protrusion 41 and theannular recess 42 are complementary with each other. Anannular recess 43 is formed on the outer circumferential portion of theouter end surface 147 of thechamber housing 14. Anannular protrusion 44 is formed on the end surface 37 of thecircumferential wall 36 of themotor housing 15. Theannular protrusion 43 and theannular recess 44 are complementary with each other. Theannular protrusions annular protrusion 39. Theannular recesses annular recess 40. As the compressor is seen in a cross-sectional view along the direction of theaxis 161 of thedrive shaft 16, theannular protrusion 42 is received in theannular recess 41 while theannular protrusion 44 is received in theannular recess 43. - In the first embodiment, the following effects are obtained.
- As shown in FIG. 3(b), when the
swash plate housing 12 and thecylinder block 13 are assembled, theend surface 29 and theend surface 30 approach with each other to have a distance which is nearly equal to the thickness T of thegasket 31. The height K1 of theannular protrusion 39 is smaller than the thickness T of thegasket 31 in one preferred embodiment. Therefore, the protrudingedges 393, 394 and the base edges 403, 404 approach with each other to have intervals t which are smaller than the thickness T of thegasket 31. Accordingly, as shown in FIGS. 3(a) and 3(b), the protrudingedges 393 and 394 contact thefirst seal surface 314 of theseal layer 312. In the same way, the base edges 403 and 404 contact thesecond seal surface 315 of theseal layer 313. In the above assembled state, the inner protrudingedge 393 pushes thegasket 31 towards theend surface 30 outside theinner base edge 403 with respect to theaxis 161 which is shown in FIG. 1, while theinner base edge 403 pushes thegasket 31 towards theend surface 29 inside the inner protrudingedge 393 with respect to theaxis 161. In a substantially similar manner, the outer protruding edge 394 pushes thegasket 31 towards theend surface 30 inside theouter base edge 404 with respect to theaxis 161, while theouter base edge 404 pushes thegasket 31 towards theend surface 29 outside the outer protruding edge 394 with respect to theaxis 161. - As a result, as shown in FIG. 3(b), the
annular gasket 31 is deformed in a direction of the thickness of theannular gasket 31 or in a direction of the annular protrusion. The deformation is made over all circumferences of theannular gasket 31. Theannular gasket 31 is deformed against rigidity of thebase plate 311 over all circumferences of theannular gasket 31. At this time, the protrudingedges 393, 394 press-contact theseal layer 312 and the base edges 403, 404 press-contact theseal layer 313. The protruding ends 393, 394 and the base ends 403, 404 are linear contacting portions and increase pressure against the seal layers 312 and 313 when press-contacted. Such high-pressure prevents refrigerant in thehousing assembly 10 from leaking through between thegasket 31 and theend surface 29 as well as between thegasket 31 and theend surface 30. - Carbon dioxide is used in higher pressure than fluoro series. Carbon dioxide in the high-pressure permeates into a seal member made of rubber. When carbon dioxide decreases its pressure, carbon dioxide in the seal member expands to damage the seal member. This damage deteriorates function of the seal member.
- The
gasket 31 is formed by affixing the seal layers 312 and 313 made of rubber to both surfaces of thebase plate 311. As thickness of the seal layers 312 and 313 is decreased, little carbon dioxide in high-pressure permeates into the seal layers 312 and 313. For the above reason, foaming is substantially reduced. Accordingly, the seal layers 312 and 313 are not damaged. - When the
annular protrusion 39 and theannular recess 40 are employed, contacting portions increase pressure against the seal layers 312 and 313. The above contacting portions are easily formed. - The
gasket 31 is flat. Therefore, both surfaces of thegasket 31 correspond to contact theend surface 29 or theend surface 30. In other words, theseal layer 312 contacts theend surface 29 while theseal layer 312 contacts theend surface 30. Theseal layer 313 contacts theend surface 29 while theseal layer 313 contacts theend surface 30. Accordingly, thegasket 31 is convenient to use. - The
annular gasket 31 has thickness that is much smaller than a diameter of theannular gasket 31 and is easily deformed equally over all circumferences of theannular gasket 31. - The
annular gaskets annular gasket 31. Theannular protrusions annular protrusion 39. Theannular recesses annular recess 40. - A second preferred embodiment of the present invention will be described with reference to FIGS.4, 4(a) and 4(b). The same reference numerals of the first preferred embodiment are applied to substantially the same components in the second preferred embodiment.
- An
annular protrusion 45 is formed on theend surface 29 of thecircumferential wall 28 of theswash plate housing 12. Anannular indentation 46 is formed on the outer circumferential portion of theend surface 30 of thecylinder block 13. Theannular protrusion 45 has a protrusion with a single step on theend surface 29 which is a securing portion. Theindentation 46 forms a recess with a single step on the outer circumferential portion which is a securing portion. Theannular protrusion 45 and theannular indentation 46 are complementary with each other. Height K2 of theannular protrusion 45 is smaller than the thickness T of thegasket 31. Depth F2 of theannular indentation 46 is substantially equal to the height K2 of theannular protrusion 45. - A width H4 of the
annular indentation 46 is larger than a width H3 of theannular protrusion 45. A diameter of thestep 451 of theannular protrusion 45 is larger than a diameter of thestep 461 of theannular indentation 46. When the compressor is seen in a cross-sectional view along the direction of theaxis 161 of thedrive shaft 16, thestep 451 of theannular protrusion 45 is positioned further away from thedrive shaft 16 than thestep 461 of theannular indentation 46. When the compressor is seen in a cross-sectional view along the direction of theaxis 161 of thedrive shaft 16, theannular protrusion 45 is received by theannular indentation 46. - As shown in FIG. 4(a), when the
swash plate housing 12 and thecylinder block 13 are assembled, theannular gasket 31 is deformed. In this state, the protrudingedge 452 of thestep 451 of theannular protrusion 45 press-contacts theseal layer 312 and the base edges 462 of thestep 461 of theannular indentation 46 press-contacts theseal layer 313. The protrudingedge 452 and thebase edge 462 are linear contacting portions and increase pressure against the seal layers 312 and 313 when press-contacted. Such high-pressure prevents the refrigerant in thehousing assembly 10 from leaking through between theannular gasket 31 and theend surface 29 as well as between theannular gasket 31 and theend surface 30. - A third preferred embodiment of the present invention will be described with reference to FIG. 5. The same reference numerals of the first preferred embodiment are applied to substantially the same components of the third preferred embodiment.
- An
annular protrusion 47 has a triangular shape with a pair oftapers tapers annular protrusion 47 which is a first contacting portion and press-contact theseal layer 312 of theannular gasket 31. An annular recess 48 has a pair oftapers tapers end surface 30 on a pair ofedge portions seal layer 313 of theannular gasket 31. Theannular protrusion 47 and the annular recess 48 are complementary with each other. - A fourth preferred embodiment of the present invention will be described with reference to FIG. 6. The same reference numerals of the first preferred embodiment are applied to substantially the same components of the fourth preferred embodiment.
- An
annular protrusion 49 has a convex or a semicircular shape in a radial cross section. Anannular recess 50 forms a concave or a semicircular shape in the radial cross section. Theannular protrusion 49 and theannular recess 50 are complementary with each other. A top 491 of theannular protrusion 49 is a first contacting portion and press-contacts theseal layer 312 of theannular gasket 31. A partial circle of theannular recess 50 is formed on theend surface 30 between a pair ofedge portions seal layer 313 of theannular gasket 31. - A fifth preferred embodiment of the present invention will be described with reference to FIGS.7, 7(a), 7(b). The same reference numerals of the first preferred embodiment are applied to substantially the same components of the fifth preferred embodiment.
- The
suction valve 241 is formed on asuction valve plate 24A. Thesuction valve plate 24A is also a gasket. Thegasket 24A includes abase plate 242 and seallayers base plate 242. Thebase plate 242 is made of metal while the seal layers 243, 244 are made of rubber. Theannular recess 41 is formed on thecylinder block 13. Theannular recess 41 forms aninner base edge 413 with aninner step 411 and anouter base edge 414 with anouter step 412 with respect to theaxis 161 which is shown in FIG. 1. The base edges 413, 414 are second contacting portions which contact asecond seal surface 246 of thesuction valve plate 24A. Theannular protrusion 42 is formed on thechamber housing 14. The annular protrusion has an innerprotruding edge 423 with aninner step 421 and an outer protrudingedge 424 with anouter step 422 with respect to theaxis 161. The protruding edges 423, 424 are first contacting portions which contact afirst seal surface 245 of thesuction valve plate 24A. Thesuction valve plate 24A is flat. When thecylinder block 13 and thechamber housing 14 are assembled, an outer circumferential portion of thesuction valve plate 24A is deformed over all circumferences of theannular gasket 31. In the above described preferred embodiment, since thesuction valve plate 24A is also used as a gasket, the number of parts is reduced. - In the present invention, the following alternative embodiments are also practiced.
- The present invention is applied to a variable displacement compressor which is disclosed in Japanese Unexamined Patent Publication No. 2000-170656. The variable displacement compressor has a control valve housing and a compressor housing. The present invention is applied to a seal between the control valve housing and the compressor housing using a gasket. In an alternative embodiment, the control valve housing is a first member and the compressor housing is a second member. The control valve housing and the compressor housing are secured to each other.
- The present invention is not applied only to a swash plate type compressor, but also to a scroll type compressor, a vane type compressor and other types of compressors.
- As described above, in the present invention, a seal structure used in a compressor has a first member, a second member and a seal member with rigidity. The first member has a surface in a first shape. The first shape has at least a first contacting portion. The second member has a surface in a second shape. The second shape has at least a second contacting portion. The first shape and the second shape are complementary with each other. The seal member has a first seal surface and a second seal surface. The seal member is located between the first contacting portion and the second contacting portion. The seal member has a sufficient area to cover at least the first contacting portion and the second contacting portion. The seal member is press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member. Accordingly, the single seal member is placed between an annular portion of the first member and a corresponding annular portion of the second member to closely seal the first member and the second member.
- The present examples and embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein but may be modified within the scope of the appended claims.
Claims (19)
1. A seal structure used in a compressor comprising:
a first member having a surface in a first shape having at least a first contacting portion;
a second member having a surface in a second shape having at least a second contacting portion, the first shape and the second shape being complementary with each other; and
a seal member with a rigidity having a first seal surface and a second seal surface, said seal member being located between said first contacting portion and said second contacting portion, said seal member having a sufficient area to cover at least the first contacting portion and the second contacting portion, said seal member being press-contacted and correspondingly deformed by the first contacting portion and the second contacting portion, thereby creating a seal between the first member and the second member.
2. The seal structure according to claim 1 wherein the first shape is a protrusion and the second shape is a recess to receive the protrusion.
3. The seal structure according to claim 2 wherein the protrusion and the recess are square.
4. The seal structure according to claim 2 wherein the protrusion and the recess are triangular.
5. The seal structure according to claim 2 wherein the protrusion and the recess are circular.
6. The seal structure according to claim 1 wherein the first shape is a protrusion, and wherein the second shape is an indentation to receive the protrusion.
7. The seal structure according to claim 2 wherein thickness of said seal member is larger than height of the protrusion.
8. The seal structure according to claim 6 wherein thickness of said seal member is larger than height of the protrusion, the height of the protrusion being substantially equal to depth of the indentation.
9. The seal structure according to claim 1 wherein said first member and said second member are respectively a swash plate housing and a cylinder block.
10. The seal structure according to claim 1 wherein said seal member has a rigid base plate and rubber seal layers on the rigid base plate.
11. The seal structure according to claim 1 wherein said seal member is flat.
12. The seal structure according to claim 1 wherein said seal member is a valve plate.
13. The seal structure according to claim 1 wherein the first contacting portion, the second contacting portion and said seal member are formed in a closed shape.
14. A seal structure used in a compressor comprising:
a first member having an annular first contacting portion;
a second member having an annular second contacting portion; and
an annular seal member with a predetermined range of rigidity having a first seal surface for contacting the first contacting portion and a second seal surface for contacting the second contacting portion, wherein said annular seal member is press-contacted and deformed by the first contacting portion and the second contacting portion, whereby said annular seal member creates a seal between said first member and said second member.
15. The seal structure according to claim 14 wherein the first contacting portion is an edge of a protrusion and the second contacting portion is an edge of a recess.
16. The seal structure according to claim 15 wherein the protrusion is in a square shape and the recess is in a square shape to receive the protrusion.
17. The seal structure according to claim 15 wherein the protrusion is in a triangular shape and the recess is in a triangular shape to receive the protrusion.
18. The seal structure according to claim 15 wherein the protrusion is in a circular shape and the recess is in a circular shape to receive the protrusion.
19. The seal structure according to claim 15 wherein the recess is in an indent shape to receive the protrusion.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000308862A JP2002115654A (en) | 2000-10-10 | 2000-10-10 | Seal structure of compressor |
JP2000-308862 | 2000-10-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20020041812A1 true US20020041812A1 (en) | 2002-04-11 |
Family
ID=18789112
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/971,479 Abandoned US20020041812A1 (en) | 2000-10-10 | 2001-10-05 | Seal structure for compressor |
Country Status (3)
Country | Link |
---|---|
US (1) | US20020041812A1 (en) |
EP (1) | EP1197687A3 (en) |
JP (1) | JP2002115654A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090010786A1 (en) * | 2006-01-25 | 2009-01-08 | Tatsuya Koide | Electrically-Driven Compressor |
CN103282660A (en) * | 2011-06-09 | 2013-09-04 | 三菱重工业株式会社 | Electric compressor |
US9121276B2 (en) | 2012-07-23 | 2015-09-01 | Emerson Climate Technologies, Inc. | Injection molded seals for compressors |
US9343940B2 (en) | 2012-05-30 | 2016-05-17 | Kabushiki Kaisha Toyota Jidoshokki | Motor-driven compressor housing, cover, and seal |
US20160353595A1 (en) * | 2014-03-20 | 2016-12-01 | Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. | Inverter-integrated electric compressor |
US20170005539A1 (en) * | 2015-07-01 | 2017-01-05 | Denso Corporation | Drive apparatus |
US9605677B2 (en) | 2012-07-23 | 2017-03-28 | Emerson Climate Technologies, Inc. | Anti-wear coatings for scroll compressor wear surfaces |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2004081382A1 (en) * | 2003-03-14 | 2004-09-23 | Zexel Valeo Climate Control Corporation | Compressor |
JP5552665B2 (en) * | 2006-01-25 | 2014-07-16 | 株式会社豊田自動織機 | Electric compressor |
KR101069692B1 (en) * | 2009-04-16 | 2011-10-05 | 주식회사 두원전자 | Reciprocating compressor |
KR102210913B1 (en) * | 2020-01-09 | 2021-02-02 | 주식회사 현대케피코 | actuator |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6427479B1 (en) * | 2000-03-10 | 2002-08-06 | Sanyo Electric Co., Ltd. | Refrigerating device utilizing carbon dioxide as a refrigerant |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1715854A (en) * | 1923-03-06 | 1929-06-04 | Standard Dev Co | Fluid-tight joint |
GB942447A (en) * | 1959-04-27 | 1963-11-20 | English Electric Co Ltd | Improvements relating to joints between adjacent members such as pipes |
US4416190A (en) * | 1979-12-13 | 1983-11-22 | Diesel Kiki Co., Ltd. | Seal for compressor |
US5022833A (en) * | 1989-12-06 | 1991-06-11 | Tecumseh Products Company | Single piece gasket valve plate assembly |
JP3102292B2 (en) | 1995-03-23 | 2000-10-23 | 株式会社豊田自動織機製作所 | Reciprocating piston compressor |
JPH0942156A (en) | 1995-07-25 | 1997-02-10 | Mitsubishi Heavy Ind Ltd | Motor compressor |
JP3860311B2 (en) | 1997-10-21 | 2006-12-20 | カルソニックカンセイ株式会社 | Swash plate compressor |
JP3849330B2 (en) | 1998-12-03 | 2006-11-22 | 株式会社豊田自動織機 | Compressor seal structure and compressor |
-
2000
- 2000-10-10 JP JP2000308862A patent/JP2002115654A/en active Pending
-
2001
- 2001-10-05 US US09/971,479 patent/US20020041812A1/en not_active Abandoned
- 2001-10-09 EP EP01124677A patent/EP1197687A3/en not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6427479B1 (en) * | 2000-03-10 | 2002-08-06 | Sanyo Electric Co., Ltd. | Refrigerating device utilizing carbon dioxide as a refrigerant |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180066659A1 (en) * | 2006-01-25 | 2018-03-08 | Kabushiki Kaisha Toyota Jidoshokki | Electrically-driven compressor |
US10371147B2 (en) * | 2006-01-25 | 2019-08-06 | Kabushiki Kaisha Toyota Jidoshokki | Electrically-driven compressor |
US20090010786A1 (en) * | 2006-01-25 | 2009-01-08 | Tatsuya Koide | Electrically-Driven Compressor |
CN103282660A (en) * | 2011-06-09 | 2013-09-04 | 三菱重工业株式会社 | Electric compressor |
US10151306B2 (en) | 2011-06-09 | 2018-12-11 | Mitsubishi Heavy Industries, Ltd. | Electric compressor |
US9343940B2 (en) | 2012-05-30 | 2016-05-17 | Kabushiki Kaisha Toyota Jidoshokki | Motor-driven compressor housing, cover, and seal |
US9605677B2 (en) | 2012-07-23 | 2017-03-28 | Emerson Climate Technologies, Inc. | Anti-wear coatings for scroll compressor wear surfaces |
US9121276B2 (en) | 2012-07-23 | 2015-09-01 | Emerson Climate Technologies, Inc. | Injection molded seals for compressors |
US20160353595A1 (en) * | 2014-03-20 | 2016-12-01 | Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. | Inverter-integrated electric compressor |
US10182506B2 (en) * | 2014-03-20 | 2019-01-15 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Inverter-integrated electric compressor |
CN106329797A (en) * | 2015-07-01 | 2017-01-11 | 株式会社电装 | Drive apparatus |
US20170005539A1 (en) * | 2015-07-01 | 2017-01-05 | Denso Corporation | Drive apparatus |
US10340765B2 (en) * | 2015-07-01 | 2019-07-02 | Denso Corporation | Drive apparatus having motor unit received in motor case |
Also Published As
Publication number | Publication date |
---|---|
EP1197687A2 (en) | 2002-04-17 |
JP2002115654A (en) | 2002-04-19 |
EP1197687A3 (en) | 2003-11-26 |
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