EP1566544A2 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- EP1566544A2 EP1566544A2 EP05003444A EP05003444A EP1566544A2 EP 1566544 A2 EP1566544 A2 EP 1566544A2 EP 05003444 A EP05003444 A EP 05003444A EP 05003444 A EP05003444 A EP 05003444A EP 1566544 A2 EP1566544 A2 EP 1566544A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- thermal insulating
- insulating member
- discharge
- compressor
- chamber
- 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.)
- Granted
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Classifications
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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
- F04B27/1009—Distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2251/00—Material properties
- F05C2251/04—Thermal properties
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/20—Resin
Definitions
- the present invention relates to a compressor which introduces a low-pressure compressible fluid for compression and discharges a compressed compressible fluid.
- a swash plate type compressor is generally known as a compressor for use in a vehicle air conditioning apparatus.
- a compressor of this type is disclosed in Japanese Unexamined Patent Publication No. 5-164042.
- the compressor includes a cylinder block which forms therein a cylindrical working chamber (or compression chamber) in which a piston is received for compressing a compressible fluid such as refrigerant gas.
- the compressor also includes a housing which covers the working chamber of the cylinder block and a valve port plate which is interposed between the housing and the cylinder block.
- the valve port plate has a suction port through which a low-pressure compressible fluid is introduced from a suction chamber formed in the housing into the working chamber.
- the valve port plate has also a discharge port through which a compressible fluid compressed by the piston is discharged into a discharge chamber formed in the housing.
- the compressor has also a discharge valve plate (or discharge plate) interposed between the valve port plate and the housing and made of a metal.
- the discharge valve plate has a plurality of discharge valves which is integrally formed with the discharge valve plate. When a compressed compressible fluid with high pressure is discharged through the discharge port, the discharge valve may be deformed in excess of the elastic limit of the discharge valve plate. Therefore, the compressor has a retainer which is formed on the side opposite to the discharge port with respect to the discharge valve for restricting the maximum opening degree of the discharge valve so that the opening degree is within the elastic limit of the discharge valve plate.
- this compressor has a partition which is formed in the housing so as to define the discharge chamber and the suction chamber, and an annular groove is formed in the partition which serves as a thermal insulating member for preventing the heat transfer of the compressible fluid in the discharge chamber to the suction chamber.
- a compressor which prevents the heat transfer of the compressed compressible fluid in the discharge chamber to the suction chamber in a similar manner is disclosed in Japanese Unexamined Patent Publication No. 2004-11531. Further, another compressor which uses rubber or resin serving as thermal insulating means is disclosed in Japanese Unexamined Patent Publication No. 2002-235667.
- the present invention is directed to a compressor having a thermal insulating member which prevents the heat transfer of compressible fluid in a discharge chamber to a suction chamber while serving as a retainer, thereby enabling reduction of the number of parts, simplification of the compressor, or reduction of the size of the compressor while maintaining the compression efficiency of the compressor.
- a compressor includes a suction chamber, a working chamber, a discharge chamber, a discharge valve and a thermal insulating member.
- a low-pressure compressible fluid resides in the suction chamber.
- the low-pressure compressible fluid in the suction chamber is introduced into the working chamber and is compressed to a predetermined pressure.
- the compressed compressible fluid in the working chamber is discharged into the discharge chamber.
- the discharge valve is interposed between the working chamber and the discharge chamber.
- the thermal insulating member is disposed in the discharge chamber.
- the thermal insulating member has an opening restricting portion for restricting the maximum opening degree of the discharge valve.
- the compressor according to the first preferred embodiment is a variable displacement type compressor which uses carbon dioxide as a compressible fluid.
- FIG. 1 shows a compressor 10 of the first embodiment.
- the compressor 10 includes a compressor housing 11 which forms the outer shell of the compressor 10.
- the compressor housing 11 includes a cylinder block 12 in which a plurality of cylinder bores 12a is formed, a front housing 13 which is joined to the front end of the cylinder block 12 and a rear housing 14 which is joined to the rear end of the cylinder block 12.
- the front housing 13, the cylinder block 12 and the rear housing 14 of the compressor housing 11 are made of aluminum-based metal to reduce the compressor weight.
- a plurality of through bolts 16 extends through the front housing 13, the cylinder block 12 and the rear housing 14 and tightens those components together in the axial direction thereof, thereby integrally fixing those components to form the compressor housing 11.
- the front housing 13 and the cylinder block 12 cooperate to define a crank chamber 17 whose rear side is closed by the cylinder block 12.
- a rotatable drive shaft 18 extends through the crank chamber 17 at the center thereof.
- the drive shaft 18 is supported at the front portion thereof by a radial bearing 19 which is disposed in the front housing 13 and at the rear portion thereof by a radial bearing 20 which is disposed in the cylinder block 12.
- a shaft seal mechanism 33 is provided on the front side of the radial bearing 19 in sliding contact with the outer peripheral surface of the drive shaft 18.
- the shaft seal mechanism 33 includes a lip seal member and a holder which holds the lip seal member, thereby preventing compressible fluid in the crank chamber 17 from leaking through a gap between the front housing 13 and the drive shaft 18.
- a lug plate 21 is fixed to the drive shaft 18 in the crank chamber 17 for rotation therewith.
- a swash plate 23 which forms a displacement changing mechanism 22 is supported by the drive shaft 18 at the rear side of the lug plate 21 so as to slide along and incline with respect to the axis of the drive shaft 18.
- a hinge mechanism 24 is interposed between the swash plate 23 and the lug plate 21, and the swash plate 23 is connected to the lug plate 21 and the drive shaft 18 through the hinge mechanism 24 for synchronous rotation therewith and inclination with respect thereto.
- a coil spring 25 is provided around the drive shaft 18 between the lug plate 21 and the swash plate 23, and a tubular body 26 is slidably fitted on the drive shaft 18 and urged rearward by the coil spring 25.
- the swash plate 23 is constantly pushed rearward by the coil spring 25 through the tubular body 26 in such a way the swash plate 23 is urged in the direction which reduces inclination angle of the swash plate 23.
- the inclination angle of the swash plate 23 is an angle between a plane perpendicular to the axial direction of the drive shaft 18 and a plane of the swash plate 23.
- a stopper 23a protrudes from the front side of the swash plate 23, and as shown in FIG.
- a retaining ring 27 is installed on the drive shaft 18 on the rear side of the swash plate 23, and a coil spring 28 is provided around the drive shaft 18 on the front side of the retaining ring 27.
- the contact of the swash plate 23 with the coil spring 28 restricts the position of the minimum inclination of the swash plate 23.
- a single-headed piston 29 is received in each cylinder bore 12a of the cylinder block 12 for reciprocation therein, and a neck portion of each piston 29 engages with the periphery of the swash plate 23 through a corresponding pair of shoes 30.
- a displacement control valve 32 is provided in the rear housing 14 which is operable to adjust the stroke of the piston 29 or the displacement of the compressor 10 by changing the angle of inclination of the swash plate 23.
- the rear housing 14, a valve port plate 35 and a suction valve plate 34 which are interposed between the rear housing 14 and the cylinder block 12, a discharge valve plate 36 and a thermal insulating member 37 will now be described.
- the rear housing 14 which is joined to the rear end of the cylinder block 12 has a suction chamber 14a formed in the rear housing 14 and a discharge chamber 14b in which the thermal insulating member 37, which will be described in detail later, is provided.
- the valve port plate 35 forms a working chamber 31 in each cylinder bore 12a with the corresponding piston 29.
- the valve port plate 35 has a suction port 35a which is in communication with the suction chamber 14a in the rear housing 14 and a discharge port 35b which is in communication with the discharge chamber 14b in the rear housing 14.
- the discharge port 35b serves as a valve port.
- the suction valve plate 34 is a plate which has suction valves (not shown) interposed between the working chambers 31 and the suction ports 35a
- the discharge valve plate 36 is a plate which has reed type discharge valves 36a interposed between the discharge ports 35b and the discharge chambers 14b.
- the thermal insulating member 37 is disposed in the discharge chamber 14b of the rear housing 14 and has a discharge space 37a formed in the thermal insulating member 37.
- the thermal insulating member 37 is provided to prevent the heat transfer of the compressible fluid in the discharge space 37a to the suction chamber 14a.
- the thermal insulating member 37 has an opening restricting portion 37b for restricting the maximum opening degree of the discharge valve 36a.
- valve plates 34, 36 are disposed between the rear housing 14 and the cylinder block 12 with the valve port plate 35 interposed therebetween. That is, the suction valve plate 34 is located on the front side of the valve port plate 35 and the discharge valve plate 36 is located on the opposite rear side thereof.
- the thermal insulating member 37 is disposed on the side of the rear housing 14 with respect to the discharge valve plate 36.
- the suction valve plate 34, the valve port plate 35, the discharge valve plate 36 and the thermal insulating member 37 are arranged in this order from the front side, and a bolt 38 extends through the valve plates 34, 36, the valve port plate 35 and the thermal insulating member 37.
- a nut 40 is screwed on the bolt 38 for fastening the valve plates 34, 36, the valve port plate 35 and the thermal insulating member 37 by way of two disc springs 39.
- the thermal insulting member 37 is constantly urged against the discharge valve plate 36 by the resilient force of the disc springs 39.
- the disc springs 39 are used as the urging member for providing urging force to the thermal insulating member 37, members other than the disc springs 39 may be used, such as resilient member made of rubber-based material or resilient sealing member.
- the suction chamber 14a is formed in radially outer region of the rear housing 14 in communication with the cylinder bore 12a via the suction port 35a formed through the valve port plate 35.
- the discharge chamber 14b in which the thermal insulating member 37 is provided, is formed in radially inner region of the rear housing 14.
- the discharge chamber 14b and the suction chamber 14a are separated sealingly from each other by a partition 14c.
- the discharge space 37a is formed in the thermal insulating member 37 so as to face the discharge valve plate 36.
- the discharge valve plate 36 is made of a thin metal sheet which has the reed type discharge valve 36a for opening and closing the discharge port 35b formed through the valve port plate 35.
- the discharge valve 36a corresponds to each of the discharge ports 35b which is correspond to the cylinder bore 12a, and a proximal end 361 of the discharge valve 36a which is located on the center of the rear housing 14 is fixed between the valve port plate 35 and the thermal insulating member 37 by being pressed by the thermal insulating member 37 which is urged frontward by the disc springs 39.
- the discharge valve 36a is flexible as the chain line shown in FIG. 2, and the maximum opening degree of the discharge valve 36a is restricted by contact thereof with the opening restricting portion 37b of the thermal insulating member 37.
- FIG. 2 shows a front view of the thermal insulating member 37 as seen from the discharge valve plate 36 (drawing on the left).
- FIG. 2 also shows a longitudinal-sectional view of the thermal insulating member 37 drawing on the right).
- the valve port plate 35 and the discharge valve plate 36 are illustrated by solid and chain lines.
- the thermal insulating member 37 has a substantially disk-like shape.
- the thermal insulating member 37 also has a plurality of recesses 37c arranged circumferentially in facing to the discharge valve plate 36 and each having substantially a sector shape. The recesses 37c are formed in the thermal insulating member 37 adjacent to the periphery of the thermal insulating member 37.
- the opening restricting portion 37b is formed between any two adjacent recesses 37c and a communication groove 37d is formed adjacent to the outer periphery of the recesses 37c for communication between the recesses 37c.
- these recesses 37c and the communication grooves 37d form the discharge space 37a.
- the opening restricting portion 37b has a curved surface as shown in the cross section of FIGS. 1 and 2, so that no harmful force is applied to the discharge valve 36a when the discharge valve 36a is fully opened in contact with the opening restricting portion 37b.
- one of the recesses 37c of the thermal insulating member 37 has an outlet 37e which is in communication with a discharge piping (broken line shown in FIG. 1) connected to an external refrigerant circuit.
- the outlet 37e is formed on the one recess 37c.
- the thermal insulating member 37 prevents the heat transfer of the compressible fluid in the discharge space 37a to the rear housing 14 including the suction chamber 14a, because the thermal insulating member 37 is made of resin material which has a smaller heat transfer coefficient than the rear housing 14 which is made of aluminum-based metal in the present embodiment.
- PPS polyphenylene sulfide
- a contacted portion 371 formed in the thermal insulating member 37 is contacted with the proximal end 361 of the discharge valve 36a, that is, the contacted portion 371 is pressed against the proximal end 361.
- This contacted portion 371 is defined by a circular region of the thermal insulating member 37, as shown by latticed hatching in FIG. 2, which ranges from the center thereof to the opening restricting portion 37b.
- the discharge valve plate 36 is kept in tight contact with the thermal insulating member 37 at the contacted portion 371 thereof, so that irregular movement of the discharge valve 36a relative to the valve port plate 35 is prevented when the discharge valve 36a is opened and closed.
- each piston 29 is reciprocated through the shoes 30.
- the compressible fluid in the suction chamber 14a is drawn into the working chamber 31 in the cylinder bore 12a through the suction valve.
- the compressible fluid in the working chamber 31 is compressed to a predetermined pressure, and then discharged into the discharge space 37a through the discharge valve 36a.
- the compressible fluid in the discharge space 37a is then high in temperature and pressure, the heat transfer of the compressible fluid in the discharge space 37a to the suction chamber 14a is prevented by the thermal insulating member 37, thereby preventing temperature rise of the low-pressure compressible fluid in the suction chamber 14a.
- the discharge valve 36a is not opened or bent in excess of its elastic limit by the contact with the opening restricting portion 37b of the thermal insulating member 37.
- the compressible fluid discharged into the discharge space 37a of the thermal insulating member 37 is discharged from the outlet 37e to the discharge piping through the communication groove 37d, which is in communication with the adjacent recesses 37c.
- the compressor 10 of the first preferred embodiment has the following advantageous effects.
- a compressor 50 according to a second preferred embodiment of the present invention will now be described with reference to FIGS. 3 and 4.
- the compressor 50 according to the second preferred embodiment is different from the compressor 10 according to the first preferred embodiment in that a discharge chamber 54b is formed in radially outer region of a rear housing 54 and that a suction chamber 54a is formed in radially inner region thereof.
- the drawings for the second embodiment use like reference numerals or symbols to denote like parts or elements of the first embodiment. Explanation of those parts which are common to the first and second embodiments is omitted, and the explanation of the first embodiment is incorporated in the second preferred embodiment. Therefore, the following description will deal with mainly the differences from the first preferred embodiment.
- the cylinder block 12 is joined at the rear end thereof to the front end of the rear housing 54 with a suction valve plate 53, a discharge valve plate 56 and a valve port plate 55 interposed therebetween.
- the suction valve plate 53 is located on the front side of the valve port plate 55 and the discharge valve plate 56 is located on the opposite rear side thereof.
- the discharge chamber 54b is annularly formed.
- An annular thermal insulating member 57 which forms a discharge space 57a is disposed in the discharge chamber 54b.
- a suction chamber 54a is formed in the radially inner region of the rear housing 54.
- the valve port plate 55 has a suction port 55a corresponding to the suction chamber 54a and a discharge port 55b that serves as a valve port through the valve port plate 55.
- the discharge port 55b corresponds to the discharge space 57a formed by the thermal insulating member 57.
- the suction valve plate 53 which forms a suction valve is interposed between the suction port 55a of the valve port plate 55 and the working chamber 31.
- the discharge valve plate 56 formed annularly and having a discharge valve 56a is interposed between the discharge port 55b of the valve port plate 55 and the discharge space 57a.
- the discharge valve 56a of the discharge valve plate 56 extends from an annular proximal end 561 of the discharge valve plate 56 toward the center of the discharge valve plate 56.
- the discharge valve 56a is formed at a position corresponding to the discharge port 55b.
- the thermal insulating member 57 of the second preferred embodiment is made in the form of a gear and has a through hole 57e formed in the central region of the thermal insulating member 57.
- FIG. 4 shows a front view of the thermal insulating member 57 which is seen from the discharge valve plate 56 (drawing on the left).
- FIG. 4 also shows a longitudinal-sectional view of the thermal insulating member 57 (drawing on the right).
- the valve port plate 55 and the discharge valve plate 56 are illustrated by solid line and chain line.
- a communication groove 57c is formed in the outer peripheral portion of the thermal insulating member 57 along the outline of the gear-like shape thereof.
- the communication groove 57c substantially corresponds to the discharge space 57a.
- An opening restricting portion 57b of a bell-like shape is formed so as to be surrounded on three sides thereof by the communication groove 57c.
- the discharge valve 56a is formed so as to face the opening restricting portion 57b. Because the opening restricting portion 57b has an arched surface in cross section, the discharge valve 56a is opened along the arched surface in its maximum opening position. Thus, the discharge valve 56a is not opened in excess of its elastic limit and the discharge valve 56a is not susceptible to excess deformation or break.
- the rear housing 54 also serves as an urging member to urge the thermal insulating member 57 toward the discharge valve plate 56 through the bolts 16, thereby pressing the thermal insulating member 57 against the discharge valve plate 56.
- the proximal end 561 of the discharge valve 56a is held securely by the thermal insulating member 57 and the valve port plate 55. Therefore, the discharge valve plate 56 makes steady opening and closing motion without irregular motion when the discharge valve 56a is in its maximum opening degree.
- One of the communication grooves 57c of the thermal insulating member 57 has an outlet 57d which is in communication with a discharge piping (not shown). The outlet 57d is formed on the one communication groove 57c.
- the compressible fluid in the communication groove 57c that serves as the discharge space 57a is discharged to the discharge piping through the outlet 57d.
- a portion of the thermal insulating member 57 which is contacted with the proximal end 561 of the discharge valve 56a, that is, a contacted portion 571 is formed in the thermal insulating member 57.
- the contacted portion 571 is shown by latticed regions in FIG. 4.
- the compressor 50 of the present preferred embodiment when the piston 29 moves from its bottom dead center to its top dead center, the compressible fluid in the working chamber 31 is compressed to a predetermined pressure and then discharged into the discharge space 57a through the discharge valve 56a. Although the compressible fluid in the discharge space 57a is then high in temperature and pressure, the heat transfer of the compressible fluid to the rear housing 54 including the suction chamber 54a is prevented by the thermal insulating member 57, thereby preventing temperature rise of the low-pressure compressible fluid in the suction chamber 54a.
- the discharge valve 56a is not opened or bent in excess of its elastic limit by the contact with the opening restricting portion 57b of the thermal insulating member 57. The compressible fluid discharged into the discharge space 57a of the thermal insulating member 57 is discharged from the outlet 57d to the discharge piping.
- the compressor 50 of the second embodiment differs from the compressor 10 of the first embodiment in that the suction chamber 54a is formed in radially inner region while the discharge space 57a is formed in radially outer region of the rear housing 54, the compressor 50 having the thermal insulating member 57 offers substantially the same effects as the compressor 10.
- FIG. 5 shows only those parts of the compressor 60 which are relevant to the third embodiment.
- the compressor 60 has a suction chamber 64a which is formed in the radially outer region of a rear housing 64 and a discharge chamber 64b having a thermal insulating member 67 disposed therein is formed in the radially inner region of the rear housing 64.
- the suction chamber 64a and the discharge chamber 64b are separated from each other by a partition 64c.
- the cylinder block 12 is joined at the rear end thereof to the front end of the rear housing 64.
- a suction valve plate 63 which forms a suction valve
- a valve port plate 65 which forms a discharge port 65b serving as a valve port
- a discharge valve plate 66 which forms a discharge valve 66a are provided.
- the suction valve plate 63 is located on the front side of the valve port plate 65 and the discharge valve plate 66 is located on the rear side thereof.
- a bolt 68 extends through the center of the valve port plate 65 and the valve plates 63, 66, and a nut 69 is screwed on the bolt 68 thereby fastening the valve plates 63, 66 to the valve port plate 65.
- the thermal insulating member 67 which is disposed in the discharge chamber 64b of the rear housing 64, has a discharge space 67a, an opening restricting portion 67b, a recess 67c, a communication groove 67d and an outlet 67e, as in the case of the first embodiment.
- a thermal insulating groove 67f is further formed in the thermal insulating member 67 on the radially outer side of the communication groove 67d.
- the thermal insulating groove 67f serves an air space in the thermal insulating member 67 for thermal insulation, and the thermal insulating effect of the air space further enhances the prevention effect of the heat transfer of the compressible fluid in the discharge space 67a to the rear housing 64 including the suction chamber 64a.
- the air space which serves as thermal insulating means having a heat transfer coefficient that is smaller than that of the thermal insulating member 67 is provided in the thermal insulating member 67.
- the present preferred embodiment employs the thermal insulating groove 67f as the air space, a material whose heat transfer coefficient is smaller than that of the thermal insulating member 67 is suitably selected.
- the through bolts 16 substantially serves as the urging member.
- the thermal insulating member 67 has a recess 67g which is opened on the front side of thermal insulating member 67.
- the recess 67g is formed in the central region of the thermal insulating member 67, and accommodates therein the bolt 68 and the nut 69.
- the air space serving as the thermal insulating means whose heat transfer coefficient is smaller than that of the thermal insulating member 67 is provided in the thermal insulating member 67, thereby further enhancing the prevention effect of the heat transfer of the compressible fluid in the discharge space 67a to the suction chamber 64a.
- FIG. 6 shows only those parts of the compressor 70 which are relevant to the fourth embodiment.
- the compressor 70 has a suction chamber 74a which is formed in the radially outer region of a rear housing 74 and a discharge chamber 74b accommodating a thermal insulating member 77 disposed therein is formed in the radially inner region of the rear housing 74.
- the suction chamber 74a and the discharge chamber 74b are separated from each other by a partition 74c.
- the cylinder block 12 is joined at the rear end thereof to the front end of the rear housing 74.
- a suction valve plate 73 which forms a suction valve, a valve port plate 75 which forms a discharge port 75b serving as a valve port, a discharge valve plate 76 which forms a discharge valve 76a and a plate 78 for pressing against the discharge valve plate 76 are provided in this order between the cylinder block 12 and the rear housing 74.
- a bolt 79 extends through the center of the valve port plate 75, the valve plates 73, 76 and the plate 78.
- a nut 80 is screwed on the bolt 79 thereby fastening the discharge valve plate 76 to the valve port plate 75.
- a disc spring 81 through which the bolt 79 extends, is interposed between the plate 78 and the nut 80. The disc spring 81 urges the plate 78 against the discharge valve plate 76, and serves as the urging means.
- the thermal insulating member 77 which is disposed in the discharge chamber 74b of the rear housing 74, has a discharge space 77a, an opening restricting portion 77b, a recess 77c, a communication groove 77d and an outlet 77e, as in the case of the first embodiment. While the thermal insulating member 77 according to the present preferred embodiment is pressed against the plate 78, the thermal insulating member 77 does not directly press against a proximal end 761 of the discharge valve 76a of the discharge valve plate 76.
- the proximal end 761 of the discharge valve 76a is mainly pressed by the plate 78 which receives elastic force of the disc spring 81, and a part of the thermal insulating member 77 is merely contacted with the plate 78. Therefore, the contact between the thermal insulating member 77 and the plate 78 may be in such condition that fluid tightness of the discharge space 77a is accomplished by providing an adhesive or sealing member between the thermal insulating member 77 and the plate 78.
- the contacted portions 371, 571 which have been explained with reference to the first and second preferred embodiments do not exist in the thermal insulating member 77 of the fourth preferred embodiment.
- the opening restricting portion 77b of the thermal insulating member 77 has an arched surface, with which part of the discharge valve 36a is contacted, in cross section.
- the area of the opening restricting portion 77b with which the discharge valve 76a is contacted is smaller than that of the opening restricting portion 37b of the first preferred embodiment due to the thickness of the plate 78 interposed between the discharge valve plate 76 and the thermal insulating member 77, the opening restricting portion 77b of the thermal insulating member 77 performs the function of restricting the maximum opening degree of the discharge valve 76a substantially in the same manner as the opening restricting portion 37b.
- the thermal insulating member 77 prevents the heat transfer of the compressible fluid in the discharge space 77a to the rear housing 74 including the suction chamber 74a
- the thermal insulating member 77 restricts the maximum opening degree of the discharge valve 76a.
- the degree of freedom of selecting material of the thermal insulating member 77 for example, its strength is improved.
- the present invention is also applicable to a scroll type compressor.
- the scroll type compressor generally includes a working chamber which is formed by a fixed scroll and a movable scroll, a suction chamber from which a low-pressure fluid is introduced into the working chamber, a discharge chamber into which a high-pressure fluid compressed in the working chamber is discharged, a discharge valve interposed between the working chamber and the discharge chamber and a retainer which restricts the maximum opening degree of the discharge valve.
- the thermal insulating member By providing a thermal insulating member in which a discharge space and an opening restricting portion for restricting the opening degree of the discharge valve are formed in the discharge chamber of the scroll type compressor, the thermal insulating member can perform the function of preventing the heat transfer from the discharge space to a housing including the suction chamber and also retaining the discharge valve opening.
- variable displacement swash plate type compressor While the first through fourth embodiments have been described by way of an example of variable displacement swash plate type compressor, the present invention is applicable to a fixed displacement swash plate type compressor. At least if the compressor is constructed such that its suction chamber and discharge chamber are located relatively adjacent to each other and that a compressible fluid is discharged into the discharge chamber through a discharge valve, the present invention is applicable to the fixed displacement swash plate type compressor. Thus, types of compressor to which the present invention is applicable are not limited.
- the thermal insulating member according to the first through fourth embodiments is made of a resin material
- the thermal insulating member may be made of any material whose heat transfer coefficient is smaller than that of a housing made of a metal such as aluminum-based or ferrous metal. Any other metals or inorganic materials whose heat transfer coefficient is small may be used.
- the thermal insulating member which serves also as a retainer has a discharge space therein, the discharge space prevents the heat transfer of the compressible fluid in the discharge chamber to the suction chamber, thereby improving the performance of the compressor.
- the suction chamber may be formed by another thermal insulating member. In this case, the heat transfer of the compressible fluid in the discharge chamber to the suction chamber is further prevented by the thermal insulating member of the suction chamber side and the thermal insulating member forming the discharge space, thereby improving the compression efficiency of the compressor. Thus, the performance of the compressor is further enhanced.
- carbon dioxide which is compressed to a high pressure is employed as the compressible fluid.
- chlorofluorocarbon or Freon gas which is compressed to a pressure that is lower than that of carbon dioxide may be employed as the compressible fluid.
- kinds of compressible fluid to which the present invention is applicable are not limited.
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- Mechanical Engineering (AREA)
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- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims (13)
- A compressor includes a suction chamber in which a low-pressure compressible fluid resides, a working chamber into which the low-pressure compressible fluid in the suction chamber is introduced and in which the compressible fluid is compressed to a predetermined pressure, a discharge chamber into which the compressed compressible fluid in the working chamber is discharged, and a discharge valve interposed between the working chamber and the discharge chamber, characterized in that a thermal insulating member is disposed in the discharge chamber, and in that the thermal insulating member has an opening restricting portion for restricting the maximum opening degree of the discharge valve.
- The compressor according to claim 1, further comprising an urging member for pressing the thermal insulating member against the discharge valve.
- The compressor according to claim 1 or 2, wherein heat transfer coefficient of the thermal insulating member is smaller than that of a housing which forms an outer shell of the compressor.
- The compressor according to claim 2, wherein the urging member is a spring.
- The compressor according to claim 2, wherein the urging member is a housing which forms an outer shell of the compressor.
- The compressor according to any one of claims 1 through 3, further comprising a plate for pressing the discharge valve to a valve port plate.
- The compressor according to any one of claims 1 through 5, wherein the thermal insulating member has a contacted portion which is contacted with a proximal end of the discharge valve.
- The compressor according to any one of claims 1 through 7, wherein the thermal insulating member has a substantially disk-like shape.
- The compressor according to any one of claims 1 through 7, wherein the thermal insulating member has an annular shape.
- The compressor according to claim 9, wherein the thermal insulating member has a gear-like shape.
- The compressor according to any one of claims 1 through 10, wherein the thermal insulating member is made of a resin material.
- The compressor according to any one of claims 1 through 11, wherein the opening restricting portion has an arched surface in cross section.
- The compressor according to any one of claims 1 through 12, wherein the compressible fluid is a carbon dioxide.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004042324A JP2005233054A (en) | 2004-02-19 | 2004-02-19 | Compressor |
JP2004042324 | 2004-02-19 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1566544A2 true EP1566544A2 (en) | 2005-08-24 |
EP1566544A3 EP1566544A3 (en) | 2005-09-21 |
EP1566544B1 EP1566544B1 (en) | 2008-01-23 |
Family
ID=34709107
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05003444A Expired - Fee Related EP1566544B1 (en) | 2004-02-19 | 2005-02-17 | Compressor |
Country Status (4)
Country | Link |
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US (1) | US20050186087A1 (en) |
EP (1) | EP1566544B1 (en) |
JP (1) | JP2005233054A (en) |
DE (1) | DE602005004433D1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7004734B2 (en) * | 1999-12-28 | 2006-02-28 | Zexel Valco Climate Control Corporation | Reciprocating refrigerant compressor |
JP4626808B2 (en) * | 2005-04-26 | 2011-02-09 | 株式会社豊田自動織機 | Capacity control valve for variable capacity clutchless compressor |
WO2008119319A2 (en) * | 2007-03-29 | 2008-10-09 | Ixetic Mac Gmbh | Air conditioning compressor |
JP2009036069A (en) * | 2007-08-01 | 2009-02-19 | Sanden Corp | Scroll type fluid machine |
DE102014014730B4 (en) * | 2014-04-16 | 2021-05-27 | Hydac Filtertechnik Gmbh | Clogging indicator |
US9995290B2 (en) * | 2014-11-24 | 2018-06-12 | Caterpillar Inc. | Cryogenic pump with insulating arrangement |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4325680A (en) * | 1980-01-23 | 1982-04-20 | Necchi Societa Per Azioni | Valve system for encapsulated motor-compressor units |
US4450860A (en) * | 1981-02-13 | 1984-05-29 | Copeland Corporation | Discharge valve guide |
US5655898A (en) * | 1995-11-14 | 1997-08-12 | Sanden Corporation | Reed valve arrangement for a reciprocating compressor |
US6364629B1 (en) * | 1999-04-16 | 2002-04-02 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Valve structure with configured retainer |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08193575A (en) * | 1995-01-13 | 1996-07-30 | Sanden Corp | Valve plate device |
JP3757580B2 (en) * | 1996-11-25 | 2006-03-22 | 株式会社豊田自動織機 | Compressor |
WO1999011930A1 (en) * | 1997-08-29 | 1999-03-11 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Swash plate compressor |
JP2001207960A (en) * | 2000-01-25 | 2001-08-03 | Toyota Autom Loom Works Ltd | Air conditioner |
JP2004183534A (en) * | 2002-12-02 | 2004-07-02 | Sanden Corp | Compressor |
-
2004
- 2004-02-19 JP JP2004042324A patent/JP2005233054A/en not_active Withdrawn
-
2005
- 2005-02-17 EP EP05003444A patent/EP1566544B1/en not_active Expired - Fee Related
- 2005-02-17 DE DE602005004433T patent/DE602005004433D1/en not_active Expired - Fee Related
- 2005-02-18 US US11/062,291 patent/US20050186087A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4325680A (en) * | 1980-01-23 | 1982-04-20 | Necchi Societa Per Azioni | Valve system for encapsulated motor-compressor units |
US4450860A (en) * | 1981-02-13 | 1984-05-29 | Copeland Corporation | Discharge valve guide |
US5655898A (en) * | 1995-11-14 | 1997-08-12 | Sanden Corporation | Reed valve arrangement for a reciprocating compressor |
US6364629B1 (en) * | 1999-04-16 | 2002-04-02 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Valve structure with configured retainer |
Also Published As
Publication number | Publication date |
---|---|
JP2005233054A (en) | 2005-09-02 |
US20050186087A1 (en) | 2005-08-25 |
EP1566544B1 (en) | 2008-01-23 |
EP1566544A3 (en) | 2005-09-21 |
DE602005004433D1 (en) | 2008-03-13 |
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