US20150023812A1 - Variable displacement compressor with single-head pistons - Google Patents
Variable displacement compressor with single-head pistons Download PDFInfo
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- US20150023812A1 US20150023812A1 US14/327,863 US201414327863A US2015023812A1 US 20150023812 A1 US20150023812 A1 US 20150023812A1 US 201414327863 A US201414327863 A US 201414327863A US 2015023812 A1 US2015023812 A1 US 2015023812A1
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- chamber
- muffler
- opening
- end surface
- muffler chamber
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- 238000006073 displacement reaction Methods 0.000 title claims description 14
- 230000002093 peripheral effect Effects 0.000 claims abstract description 55
- 238000004891 communication Methods 0.000 claims abstract description 20
- 230000006835 compression Effects 0.000 claims description 10
- 238000007906 compression Methods 0.000 claims description 10
- 230000010349 pulsation Effects 0.000 description 20
- 238000000034 method Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
- F04B53/003—Noise damping by damping supports
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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
Definitions
- the present invention relates to a variable displacement compressor with single-head pistons.
- Japanese Patent Laid-Open No. 9-287564 discloses a conventional variable displacement compressor with single-head pistons (referred to simply as a compressor hereinafter).
- the compressor comprises a cylinder block, a front housing, a rear housing, pistons and driving means.
- the cylinder block has a plurality of cylinder bores arranged side by side in the circumferential direction and extending in parallel with each other in the axial direction.
- the front housing is fixed to one end part of the cylinder block in the axial direction.
- the front housing has a crank chamber formed therein.
- the rear housing is fixed to the other end part of the cylinder block in the axial direction.
- the rear housing has a suction chamber and a discharge chamber formed therein.
- a piston is housed in each of the cylinder bores so as to reciprocate and defines a compression chamber in a rear part of each of the cylinder bores.
- the driving means is provided in the crank chamber. The driving means can make each of the pistons reciprocate and change strokes of each of the pistons.
- the rear housing has an annular wall that separates the suction chamber and the discharge chamber from each other.
- the suction chamber is formed between the annular wall and the outer peripheral wall of the rear housing and extends in the circumferential direction to annularly surround the discharge chamber.
- the cylinder block has an outlet port through which the discharge chamber is in communication with the outside.
- a muffler is provided between the discharge chamber and the outlet port. The muffler is positioned at a position close to the outer peripheral surface of the cylinder block.
- the muffler has a muffler chamber, an inlet channel and an outlet channel. The inlet channel provides communication between the discharge chamber and the muffler chamber.
- the outlet channel provides communication between the muffler chamber and the outlet port.
- the compressor With this compressor, the refrigerating gas at high pressure flows out of the discharge chamber into the muffler chamber through the inlet channel and then flows through the outlet channel and is discharged to the outside from the outlet port. In this process, the flow of the refrigerating gas is narrowed down in the inlet channel and then expands in the muffler chamber. In this way, the compressor is configured to reduce the discharge pulsation.
- the volume of the muffler chamber needs to be increased in order for the muffler to appropriately reduce the discharge pulsation, and it is difficult to arrange a less bulky muffler in the outer peripheral part of the cylinder block.
- the present invention has been devised in view of the circumstances of the prior art described above, and an object to be attained of the present invention is to provide a variable displacement compressor with single-head pistons that can have a reduced size and appropriately reduce a discharge pulsation.
- a variable displacement compressor with single-head pistons according to the present invention comprises:
- a cylinder block having a plurality of cylinder bores that are formed side by side in a circumferential direction and extend in parallel with each other in an axial direction;
- a front housing that is fixed to one end side of the cylinder block in the axial direction and has a crank chamber formed therein;
- a rear housing that is fixed to the other end side of the cylinder block in the axial direction and has a suction chamber and a discharge chamber formed therein;
- a plurality of pistons each housed in each of the cylinder bores so as to reciprocate and defining a compression chamber in each of the cylinder bores on the other end side; and driving means that is provided in the crank chamber and is capable of making each of the pistons reciprocate and changing strokes of each of the pistons.
- the rear housing has an annular wall that separates the suction chamber and the discharge chamber from each other.
- the discharge chamber is formed between the annular wall and an outer peripheral wall of the rear housing so as to extend in the circumferential direction and annularly surround the suction chamber.
- An outlet port through which the discharge chamber is in communication with the outside, is formed in the cylinder block or the rear housing.
- a muffler is provided between the discharge chamber and the outlet port.
- the muffler has a muffler chamber, an inlet channel and an outlet channel.
- the muffler chamber is formed in the rear housing.
- the inlet channel provides communication between the discharge chamber and the muffler chamber.
- the outlet channel provides communication between the muffler chamber and the outlet port.
- the muffler chamber has a first end surface, a second end surface, and an inner peripheral surface.
- the first end surface is positioned on the one end side of the muffler chamber.
- the second end surface is positioned on the other end side of the muffler chamber.
- the inner peripheral surface has a cylindrical shape, is positioned between the first end surface and the second end surface and extends from the discharge chamber toward the other end side.
- the muffler chamber is positioned between the annular wall and the outer peripheral wall.
- the inlet channel opens in the first end surface.
- the outlet channel opens in the inner peripheral surface at a position spaced apart from the second end surface.
- FIG. 1 is a vertical cross-sectional view of a compressor according to an embodiment 1.
- FIG. 2 is a cross-sectional view of the compressor according to the embodiment 1 taken along the line II-II in FIG. 1 .
- FIG. 3 is a schematic perspective view of the compressor according to the embodiment 1, showing a configuration of an inlet channel, a first end surface, an inner peripheral surface, a second end surface, a muffler chamber and an outlet channel.
- FIG. 4 is a partially enlarged cross-sectional view of the compressor according to the embodiment 1.
- FIG. 5 is a partially enlarged cross-sectional view of a compressor according to an embodiment 2.
- FIG. 6 is a schematic perspective view of the compressor according to the embodiment 2, showing a configuration of the inlet channel, the first end surface, the inner peripheral surface, an intermediate member, a first muffler chamber, the second end surface, a second muffler chamber and the outlet channel.
- FIG. 7 is a partially enlarged cross-sectional view of a compressor according to an embodiment 3.
- FIG. 8 is a perspective view of an intermediate member of the compressor according to the embodiment 3.
- FIG. 9 is a partially enlarged cross-sectional view of a compressor according to an embodiment 4.
- FIG. 10 is a cross-sectional view of the compressor according to the embodiment 4 taken along the line X-X in FIG. 9 .
- a variable displacement compressor with single-head pistons (referred to simply as a compressor hereinafter) according to an embodiment 1 comprises a cylinder block 1 , a front housing 3 , a rear housing 5 , pistons 25 and driving means 4 .
- the cylinder block 1 has a plurality of cylinder bores 1 a that are formed side by side at regular angular intervals in the circumferential direction and extend in parallel with each other.
- Each of the cylinder bores 1 a is a cylindrical cavity that penetrates the cylinder block 1 in the front-rear direction.
- Each of the cylinder bores 1 a houses each of the pistons 25 in such a manner that the pistons 25 can reciprocate in the front-rear direction.
- the front-rear direction is an example of “axial directions” according to the present invention.
- the front side is an example of “one end side in the axial direction”, and the rear side is an example of “the other side in the axial direction”.
- the cylinder block 1 is held between the front housing 3 disposed in front thereof and the rear housing 5 disposed at the rear thereof, and fastened in this state with a plurality of bolts 7 .
- the front housing 3 is fixed to the front of the cylinder block 1
- the rear housing 5 is fixed to the rear of the cylinder block 1 .
- the front housing 3 has a crank chamber 9 formed therein.
- a valve unit 29 is disposed between the rear housing 5 and the cylinder block 1 .
- the driving means 4 comprises a drive shaft 11 , a lug plate 15 , a swash plate 17 and a link mechanism 23 , for example.
- a shaft hole 3 a is formed in the front housing 3 .
- a shaft hole 1 b is formed in the cylinder block 1 .
- the drive shaft 11 extends in the crank chamber 9 in the front-rear direction. A front end part of the drive shaft 11 protrudes to the outside of the front housing 3 through the shaft hole 3 a.
- a shaft seal device 9 s and a bearing device 10 a are fitted in the shaft hole 3 a.
- the shaft seal device 9 s seals the gap between the drive shaft 11 and the front housing 3 .
- a rear end part of the drive shaft 11 protrudes into the shaft hole 1 b.
- a bearing device 10 b is provided between the shaft hole 1 b and the rear end part of the drive shaft 11 .
- the drive shaft 11 is rotatably supported in the shaft holes 3 a and 1 b with the bearing devices 10 a and 10 b interposed therebetween.
- the lug plate 15 is press-fitted around the drive shaft 11 in the crank chamber 9 .
- a bearing device 10 c is provided between the lug plate 15 and the front housing 3 .
- a pulley 13 is fixed to the front end part of the drive shaft 11 .
- a bearing device 3 b is disposed between the pulley 13 and the front housing 3 .
- a belt 13 c which is driven by an engine or a motor of a vehicle, is wound around the pulley 13 .
- An electromagnetic clutch may be provided instead of the pulley 13 .
- the swash plate 17 is penetrated by the drive shaft 11 in the crank chamber 9 .
- the swash plate 17 is positioned behind the lug plate 15 .
- An inclination reducing spring 19 is provided on the circumference of the drive shaft 11 between the lug plate 15 and the swash plate 17 .
- a circlip 11 a is fixed to the drive shaft 11
- a return spring 21 is provided on the circumference of the drive shaft 11 between the circlip 11 a and the swash plate 17 .
- the link mechanism 23 connects the lug plate 15 and the swash plate 17 to each other in the crank chamber 9 .
- the link mechanism 23 supports the swash plate 17 in such a manner that the inclination angle of the swash plate 17 with respect to the lug plate 15 can be changed.
- a front-rear pair of shoes 27 a and 27 b is provided between each of the pistons 25 and the swash plate 17 .
- the pairs of shoes 27 a and 27 b each converts the rotation of the swash plate 17 into the reciprocation of the corresponding piston 25 in the front-rear direction.
- each of the cylinder bores 1 a a rear end surface of each of the pistons 25 faces the valve unit 29 .
- the pistons 25 each defines a compression chamber 31 in a rear part of each of the cylinder bores 1 a.
- the valve unit 29 operates to make the compression chambers 31 suck in a refrigerating gas from a suction chamber 5 a when the pistons 25 are in a suction stroke.
- the valve unit 29 also operates to confine the refrigerating gas in the compression chambers 31 when the pistons are in a compression stroke, and to make the compression chambers 31 discharge the refrigerating gas to a discharge chamber 5 b when the pistons 25 are in a discharge stroke.
- the rear housing 5 has the suction chamber 5 a, which is radially inwardly positioned, and the discharge chamber 5 b, which is radially outwardly positioned.
- the discharge chamber 5 b extends in the circumferential direction to annularly surround the suction chamber 5 a.
- the rear housing 5 also has an inlet port 5 h through which the suction chamber 5 a is in communication with the outside.
- the suction chamber 5 a is defined by an annular wall 5 m formed in the rear housing 5 .
- the discharge chamber 5 b is defined by the annular wall 5 m and an outer peripheral wall 5 n of the rear housing 5 .
- crank chamber 9 and the suction chamber 5 a are connected to each other by a bleed passage 42 .
- the crank chamber 9 and the discharge chamber 5 b are connected to each other by supply passages 44 and 46 .
- the rear housing 5 houses a volume control valve 2 .
- the volume control valve 2 is provided between the supply passages 44 and 46 .
- the opening of the volume control valve 2 is externally adjusted by power supply control, thereby controlling the balance between the amount of the refrigerating gas at high pressure introduced into the crank chamber 9 from the discharge chamber 5 b through the supply passages 44 and 46 and the amount of the refrigerating gas introduced into the suction chamber 5 a from the crank chamber 9 through the bleed passage 42 , and determining the internal pressure of the crank chamber 9 .
- the internal pressure of the crank chamber 9 changes, the difference in pressure between the crank chamber 9 and the compression chamber 31 changes, the inclination angle of the swash plate 17 changes, and accordingly, the strokes of the pistons 25 , that is, the discharge volume of the compressor is adjusted.
- An outlet port 1 h through which the discharge chamber 5 b is in communication with the outside, is provided on the outer peripheral. surface of the cylinder block 1 .
- a muffler 100 is provided between the discharge chamber 5 b and the outlet port 1 h.
- the muffler 100 has a muffler chamber 110 , an inlet channel 101 , and outlet channels 102 a and 102 b.
- the rear housing 5 has a closed-end circular hole 5 G that extends rearward from a rear wall surface 5 r of the discharge chamber 5 b.
- the cylindrical inner wall surface of the closed-end circular hole 5 G is an inner peripheral surface 113 .
- the circular bottom surface of the closed-end circular hole 5 G is a second end surface 112 positioned at the rear end of the inner peripheral surface 113 .
- a disk-shaped lid member 109 is press-fitted in the closed-end circular hole 5 G.
- a front surface of the lid member 109 is substantially flush with the rear wall surface 5 r.
- the rear surface of the lid member 109 is a first end surface 111 positioned at the front end of the inner peripheral surface 113 .
- the muffler chamber 110 is a cylindrical cavity defined by the inner peripheral surface 113 , the first end surface 111 and the second end surface 112 .
- the muffler chamber 110 is positioned between the annular wall 5 m and the outer peripheral wall 5 n.
- the rear housing 5 has a plurality of bolt insertion holes 6 , into which the bolts 7 are inserted.
- the muffler chamber 110 is positioned between two bolt insertion holes 6 a and 6 b. As shown in FIG.
- a distance A from a front end surface 5 f of the rear housing 5 to the second end surface 112 of the muffler chamber 111 is equal to or smaller than a distance B from the front end surface 5 f of the rear housing 5 to a rear end surface 5 e of the discharge chamber 5 b.
- the inlet channel 101 is a circular hole that penetrates the lid member 109 at the center thereof in the front-rear direction.
- the inlet channel 101 forms an inlet opening 101 h having a circular shape in the first end surface 111 . That is, the lid member 109 fitted inside the front part of the inner peripheral surface 113 separates the discharge chamber 5 b and the muffler chamber 110 from each other and provides the first end surface 111 , the inlet channel 101 and the inlet opening 101 h.
- the inlet channel 101 provides communication between the discharge chamber 5 b and the muffler chamber 110 .
- the outlet channel 102 a is formed in the rear housing 5 .
- the outlet channel 102 a is a hole that extends straight from a part 5 S of the front surface of the rear housing 5 positioned radially outward from the discharge chamber 5 b toward the inner peripheral surface 113 .
- the outlet channel 102 a is inclined with respect to the front-rear direction.
- the outlet channel 102 b is a hole that is formed in the valve unit 29 and the cylinder block 1 and extends straight in the front-rear direction.
- a rear end part of the outlet channel 102 b is in communication with a front end part of the outlet channel 102 a.
- a front end part of the outlet channel 102 b is in communication with the outlet port 1 h.
- the outlet channel 102 a forms an outlet opening 102 h having an elliptical shape in the inner peripheral surface 113 at a position spaced apart from the second end surface 112 .
- an inner diameter D2 of the outlet channel 102 a is larger than an inner diameter D1 of the inlet channel 101 .
- the discharge chamber 5 b of the compressor according to the embodiment 1 configured as described above is connected to a condenser via the muffler chamber 100 and the outlet port 1 h, the condenser is connected to an evaporator via an expansion valve, and the evaporator is connected to the suction chamber 5 a via the inlet port 5 h.
- the refrigerating gas is introduced from the suction chamber 5 a into the compression chamber 31 in a discharge volume corresponding to the inclination angle of the swash plate 17 and compressed therein, and then discharged into the discharge chamber 5 b.
- the refrigerating gas at high pressure in the discharge chamber 5 b flows through the inlet channel 101 into the muffler chamber 110 at the inlet opening 101 h formed in the first end surface 111 , flows out into the outlet channels 102 a and 102 b at the outlet opening 102 h formed in the inner peripheral surface 113 , and is discharged to the outside at the outlet port 1 h.
- the flow of the refrigerating gas is narrowed down in the inlet channel 101 and then expands in the muffler chamber 110 , so that the discharge pulsation can be reduced.
- the muffler chamber 110 is a cylindrical cavity defined by the cylindrical inner peripheral surface 113 , the first end surface 111 and the second end surface 112 .
- the inventors have found that the amplitude of the pulsation of the pressure of the refrigerating gas flowing into the muffler chamber 110 tends to be smaller in a part close to the inner peripheral surface 113 than in a part close to the second end surface 112 .
- the amplitude of the pulsation of the pressure of the refrigerating gas flowing from the muffler chamber 110 into the outlet channels 102 a and 102 b through the outlet opening 102 h can be smaller in the case where the outlet channel 102 a opens in the inner peripheral surface 113 at a position spaced apart from the second end surface 112 than in the case where the outlet channel 102 a opens in the second end surface 112 .
- the compressor can reduce the discharge pulsation and can accordingly reduce the volume of the muffler chamber 110 .
- the muffler 100 disposed in the rear housing 5 of this compressor can be less bulky.
- the muffler chamber 110 is positioned between the annular wall 5 m and the outer peripheral wall 5 n, the muffler 100 can be prevented from protruding in the radially outward direction of the rear housing 5 .
- the distance A from the front end surface 5 f of the rear housing 5 to the second end surface 112 of the muffler chamber 110 is set to be equal to or smaller than the distance B from the front end surface 5 f of the rear housing 5 to the rear end surface 5 e of the discharge chamber 5 b, the muffler 100 can be prevented from protruding in the axial direction of the rear housing 5 .
- the compressor according to the embodiment 1 can have a reduced size and appropriately reduce the discharge pulsation.
- the inner peripheral surface 113 and the second end surface 112 can be easily formed by forming the closed-end circular hole 5 G, which is recessed toward the rear from the discharge chamber 5 b, in the rear housing 5 .
- the outlet channel 102 a and the outlet opening 102 h can be easily formed by forming a hole that obliquely penetrates the rear housing 5 from the part 5 S of the front surface of the rear housing 5 to the inner peripheral surface 113 of the muffler chamber 110 .
- the first end surface 111 , the inlet channel 101 and the inlet opening 101 h can be easily formed by fitting the disk-shaped lid member 109 having an opening formed therein inside the inner peripheral surface 113 . Owing to these characteristics, the compressor can be manufactured at low cost.
- a compressor according to an embodiment 2 differs from the compressor according to the embodiment 1 in that the muffler 100 is additionally provided with an intermediate member 230 .
- the remainder of the configuration of the compressor according to the embodiment 2 is the same as that according to the embodiment 1.
- the same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted.
- the intermediate member 230 is fitted inside the inner peripheral surface 113 between the first end surface 111 and the second end surface 112 .
- the intermediate member 230 comprises a main body part 232 and an extension part 231 .
- the main body part 232 is disk-shaped, and the outer peripheral edge thereof is partially radially inwardly recessed to form a recessed part 232 a.
- the extension part 231 is integral with the main body part 232 .
- the extension part 231 encloses the recessed part 232 a and extends toward the front.
- a peripheral edge 231 e of the extension part 231 is in intimate contact with the inner peripheral surface 113 .
- the main body part 232 and the extension part 231 of the intermediate member 230 divide the muffler chamber 110 into a first muffler chamber 210 a positioned to the front and a second muffler chamber 210 b positioned to the rear.
- a first opening 231 h is a circular hole formed in a front part of the extension part 231 .
- the first opening 231 h penetrates the extension part 231 in the radial direction and opens into the first muffler chamber 210 a.
- the second opening 232 h is a clearance formed in a rear surface of the main body part 232 between the recessed part 232 a and the inner peripheral surface 113 , and opens into the second muffler chamber 210 b.
- the intermediate flow channel 233 is a cavity formed between the extension part 231 and the main body part 232 of the intermediate member 230 and the inner peripheral surface 113 , and intermediate flow channel 233 extends in the front-rear direction.
- the extension part 231 is in communication with the first opening 231 h at the front thereof and is in communication with the second opening 232 h at the rear thereof.
- the first opening 231 h is formed in the front part of the extension part 231 so as to penetrate the extension part 231 in the radial direction.
- the first opening 231 h may be formed in the front part of the extension part 231 at a position opposed to the first end surface 111 so as to penetrate the extension part 231 in the axial direction.
- an inner diameter D3 of the first opening 231 h is smaller than the inner diameter D2 of the outlet channel 102 a.
- the inner diameter D3 of the first opening 231 h is slightly larger than the inner diameter D1 of the inlet channel 101 .
- the refrigerating gas at high pressure in the discharge chamber 5 b flows into the first muffler chamber 210 a through the inlet channel 101 at the inlet opening 101 h, and then flows into the second muffler chamber 210 b through the first opening 231 h, the intermediate flow channel 233 and the second opening 232 h.
- the refrigerating gas then flows out into the outlet channels 102 a and 102 b through the outlet opening 102 h and is discharged to the outside through the outlet port 1 h.
- this compressor can further reduce the discharge pulsation, because the flow of the refrigerating gas is once narrowed down by the inlet channel 101 and then expanded in the first muffler chamber 210 a, and then narrowed down again by the intermediate flow channel 233 and then expanded in the second muffler chamber 210 b.
- the first muffler chamber 210 a is a substantially cylindrical cavity defined by the cylindrical inner peripheral surface 113 , the first end surface 111 positioned to the front, the main body part 232 positioned to the rear of the first end surface 111 , and the extension part 231 that is integral with the main body part 232 and extends toward the front.
- the amplitude of the pulsation of the pressure of the refrigerating gas flowing into the first muffler chamber 210 a tends to be smaller in a part close to the front of the extension part 231 than in a part close to the main body part 232 .
- the amplitude of the pulsation of the pressure of the refrigerating gas flowing into the second muffler chamber 210 b through the first opening 231 h, the intermediate flow channel 233 and the second opening 232 h can be smaller in the case where the first opening.
- 231 h opens in the front part of the extension part 231 than in the case where the first opening 231 h opens in the main body part 232 .
- the second muffler chamber 210 b is a cylindrical cavity defined by the cylindrical inner peripheral surface 113 , the second end surface 112 positioned to the rear, and the main body part 232 positioned to the front of the second end surface 112 .
- the amplitude of the pulsation of the pressure of the refrigerating gas flowing from the first muffler chamber 210 a into the second muffler chamber 210 b through the first opening 231 h, the intermediate flow channel 233 and the second opening 232 h tends to be smaller in a part close to the inner peripheral surface 113 than in a part close to the second end surface 112 .
- the amplitude of the pulsation of the pressure of the refrigerating gas flowing out of the second muffler chamber 210 b into the outlet channels 102 a and 102 b can be smaller in the case where the flow channel 102 a has the outlet opening 102 h in the inner peripheral surface 113 than in the case where the outlet channel 102 a opens in the second end surface 112 .
- the compressor according to the embodiment 2 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressor according to the embodiment 1.
- a compressor according to an embodiment 3 differs from the compressor according to the embodiment 1 in that the muffler 100 is additionally provided with three intermediate members 330 .
- the remainder of the configuration of the compressor according to the embodiment 3 is the same as that according to the embodiment 1.
- the same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted.
- the three intermediate members 330 are disk-shaped members having the same shape. Each intermediate member 330 is fitted inside the inner peripheral surface 113 side by side in the front-rear direction between the first end surface 111 and the second end surface 2 .
- the intermediate members 330 divide the muffler chamber 110 into four muffler chamber sections 310 a, 310 b, 310 c and 310 d.
- each muffler chamber section 310 a - 310 c positioned to the front of that intermediate member 330 is an example of the “first muffler chamber” according to the present invention
- each muffler chamber section 310 b - 310 d positioned to the rear of that intermediate member 330 is an example of the “second muffler chamber” according to the present invention.
- a plurality of sets of a first opening 331 , a second opening 332 and an intermediate flow channel 333 are formed in each intermediate member 330 .
- the first opening 331 , the second opening 332 and the intermediate flow channel 333 are parts of a perforated substantially funnel-shaped part protruding toward the front formed by piercing the intermediate member 330 with a sharp-pointed needle-like tool.
- the first opening 331 opens into the muffler chamber section 310 a - 310 c positioned to the front.
- the second opening 332 opens into the muffler chamber section 310 b - 310 d positioned to the rear.
- the intermediate flow channel 333 provides communication between the first opening 331 and the second opening 332 .
- the sets of the first opening 331 , the second opening 332 and the intermediate flow channel 333 formed in one of adjacent two intermediate members 330 are displaced from the sets of the first opening 331 , the second opening 332 and the intermediate flow channel 333 formed in the other of the adjacent two intermediate members 330 .
- the refrigerating gas flowing into the muffler chamber 110 sequentially passes through the muffler chamber sections 310 a to 310 d.
- the flow of the refrigerating gas is narrowed down by the set of the first opening 331 , the second opening 332 and the intermediate flow channel 333 formed in each intermediate member 330 and then expands.
- the refrigerating gas is agitated as the refrigerating gas flows in a serpentine path since the sets of the first opening 331 , the second opening 332 and the intermediate flow channel 333 are displaced from each other when viewed in the front-rear direction. As a result, the amplitude of the pulsation of the pressure of the refrigerating gas is reduced.
- the compressor according to the embodiment 3 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressors according to the embodiments 1 and 2.
- a compressor according to an embodiment 4 differs from the compressor according to the embodiment 1 in that the muffler 100 is additionally provided with an agitating member 440 .
- the remainder of the configuration of the compressor according to the embodiment 4 is the same as that according to the embodiment 1.
- the same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted.
- the agitating member 440 is inserted in the muffler chamber 110 .
- the agitating member 440 has a plurality of minute reflecting surface elements 441 whose reflecting surfaces intersect with the front-rear direction.
- the reflecting surface elements 441 are dispersed in the muffler chamber 110 by fixing the reflecting surface elements 441 onto a wire coil (not shown) at intervals and placing the coil wire in the muffler chamber 110 , for example.
- the reflecting surface elements 441 may be parts of a stainless steel scourer made of spiral-shaped chips produced in lathe machining of a stainless steel material, for example.
- the refrigerating gas flowing into the muffler chamber 110 is agitated by the plurality of minute reflecting surface elements 441 of the agitating member 440 , so that the amplitude of the pulsation of the pressure of the refrigerating gas is reduced.
- the compressor according to the embodiment 4 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressors according to the embodiments 1 to 3.
- the outlet opening 102 h is formed in the inner peripheral surface 113 at a position that is spaced apart from the second end surface 112 toward the first end surface 111 and is closer to the second end surface 112 than the first end surface 111 .
- the outlet opening 102 h may be formed in the inner peripheral surface 113 at a position that is spaced apart from the second end surface 112 toward the first end surface 111 and is closer to the first end surface 111 than the second end surface 112 .
- the inner diameter D2 of the outlet channel 102 a is larger than the inner diameter D1 of the inlet channel 101 .
- the inner diameter D2 may be smaller than or equal to the inner diameter D1.
- the distance A from the front end surface 5 f of the rear housing 5 to the second end surface 112 of the muffler chamber 110 is equal to or smaller than the distance B from the front end surface 5 f of the rear housing 5 to the rear end surface. 5 e of the discharge chamber 5 b.
- the muffler chamber 110 may be configured so that the distance A is longer than the distance B.
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The muffler has a muffler chamber formed in a rear housing, an inlet channel that provides communication between the discharge chamber and the muffler chamber, and an outlet channel that provides communication between the muffler chamber and the outlet port. The muffler chamber has a first end surface positioned on one end side of the muffler chamber, a second end surface positioned on the other end side of the muffler chamber, and an inner peripheral surface having a cylindrical shape that is positioned between the first end surface and the second end surface and extends from the discharge chamber toward the other end side. The muffler chamber is positioned between an annular wall and an outer peripheral wall. The inlet channel opens in the first end surface. The outlet channel opens in the inner peripheral surface at a position spaced apart from the second end surface.
Description
- The present invention relates to a variable displacement compressor with single-head pistons.
- Japanese Patent Laid-Open No. 9-287564 discloses a conventional variable displacement compressor with single-head pistons (referred to simply as a compressor hereinafter). The compressor comprises a cylinder block, a front housing, a rear housing, pistons and driving means. The cylinder block has a plurality of cylinder bores arranged side by side in the circumferential direction and extending in parallel with each other in the axial direction. The front housing is fixed to one end part of the cylinder block in the axial direction. The front housing has a crank chamber formed therein. The rear housing is fixed to the other end part of the cylinder block in the axial direction. The rear housing has a suction chamber and a discharge chamber formed therein. A piston is housed in each of the cylinder bores so as to reciprocate and defines a compression chamber in a rear part of each of the cylinder bores. The driving means is provided in the crank chamber. The driving means can make each of the pistons reciprocate and change strokes of each of the pistons.
- The rear housing has an annular wall that separates the suction chamber and the discharge chamber from each other. The suction chamber is formed between the annular wall and the outer peripheral wall of the rear housing and extends in the circumferential direction to annularly surround the discharge chamber. The cylinder block has an outlet port through which the discharge chamber is in communication with the outside. A muffler is provided between the discharge chamber and the outlet port. The muffler is positioned at a position close to the outer peripheral surface of the cylinder block. The muffler has a muffler chamber, an inlet channel and an outlet channel. The inlet channel provides communication between the discharge chamber and the muffler chamber. The outlet channel provides communication between the muffler chamber and the outlet port.
- With this compressor, the refrigerating gas at high pressure flows out of the discharge chamber into the muffler chamber through the inlet channel and then flows through the outlet channel and is discharged to the outside from the outlet port. In this process, the flow of the refrigerating gas is narrowed down in the inlet channel and then expands in the muffler chamber. In this way, the compressor is configured to reduce the discharge pulsation.
- With the conventional compressor described above, the volume of the muffler chamber needs to be increased in order for the muffler to appropriately reduce the discharge pulsation, and it is difficult to arrange a less bulky muffler in the outer peripheral part of the cylinder block. In this regard, with the conventional compressor, it is difficult to reduce the size of the compressor and appropriately reduce the discharge pulsation.
- The present invention has been devised in view of the circumstances of the prior art described above, and an object to be attained of the present invention is to provide a variable displacement compressor with single-head pistons that can have a reduced size and appropriately reduce a discharge pulsation.
- A variable displacement compressor with single-head pistons according to the present invention comprises:
- a cylinder block having a plurality of cylinder bores that are formed side by side in a circumferential direction and extend in parallel with each other in an axial direction;
- a front housing that is fixed to one end side of the cylinder block in the axial direction and has a crank chamber formed therein;
- a rear housing that is fixed to the other end side of the cylinder block in the axial direction and has a suction chamber and a discharge chamber formed therein;
- a plurality of pistons each housed in each of the cylinder bores so as to reciprocate and defining a compression chamber in each of the cylinder bores on the other end side; and driving means that is provided in the crank chamber and is capable of making each of the pistons reciprocate and changing strokes of each of the pistons.
- The rear housing has an annular wall that separates the suction chamber and the discharge chamber from each other.
- The discharge chamber is formed between the annular wall and an outer peripheral wall of the rear housing so as to extend in the circumferential direction and annularly surround the suction chamber.
- An outlet port, through which the discharge chamber is in communication with the outside, is formed in the cylinder block or the rear housing.
- A muffler is provided between the discharge chamber and the outlet port.
- The muffler has a muffler chamber, an inlet channel and an outlet channel. The muffler chamber is formed in the rear housing. The inlet channel provides communication between the discharge chamber and the muffler chamber. The outlet channel provides communication between the muffler chamber and the outlet port.
- The muffler chamber has a first end surface, a second end surface, and an inner peripheral surface. The first end surface is positioned on the one end side of the muffler chamber. The second end surface is positioned on the other end side of the muffler chamber. The inner peripheral surface has a cylindrical shape, is positioned between the first end surface and the second end surface and extends from the discharge chamber toward the other end side.
- The muffler chamber is positioned between the annular wall and the outer peripheral wall.
- The inlet channel opens in the first end surface.
- The outlet channel opens in the inner peripheral surface at a position spaced apart from the second end surface.
- Other aspects and advantages of the invention will be apparent from embodiments disclosed in the attached drawings, illustrations exemplified therein, and the concept of the invention.
-
FIG. 1 is a vertical cross-sectional view of a compressor according to an embodiment 1. -
FIG. 2 is a cross-sectional view of the compressor according to the embodiment 1 taken along the line II-II inFIG. 1 . -
FIG. 3 is a schematic perspective view of the compressor according to the embodiment 1, showing a configuration of an inlet channel, a first end surface, an inner peripheral surface, a second end surface, a muffler chamber and an outlet channel. -
FIG. 4 is a partially enlarged cross-sectional view of the compressor according to the embodiment 1. -
FIG. 5 is a partially enlarged cross-sectional view of a compressor according to anembodiment 2. -
FIG. 6 is a schematic perspective view of the compressor according to theembodiment 2, showing a configuration of the inlet channel, the first end surface, the inner peripheral surface, an intermediate member, a first muffler chamber, the second end surface, a second muffler chamber and the outlet channel. -
FIG. 7 is a partially enlarged cross-sectional view of a compressor according to an embodiment 3. -
FIG. 8 is a perspective view of an intermediate member of the compressor according to the embodiment 3. -
FIG. 9 is a partially enlarged cross-sectional view of a compressor according to anembodiment 4. -
FIG. 10 is a cross-sectional view of the compressor according to theembodiment 4 taken along the line X-X inFIG. 9 . - In the following, embodiments 1 to 4 of the present invention will be described with reference to the drawings. In the following description, the front-rear direction is assumed as shown in
FIG. 1 . - As shown in
FIG. 1 , a variable displacement compressor with single-head pistons (referred to simply as a compressor hereinafter) according to an embodiment 1 comprises a cylinder block 1, a front housing 3, arear housing 5,pistons 25 and driving means 4. - The cylinder block 1 has a plurality of cylinder bores 1 a that are formed side by side at regular angular intervals in the circumferential direction and extend in parallel with each other. Each of the cylinder bores 1 a is a cylindrical cavity that penetrates the cylinder block 1 in the front-rear direction. Each of the cylinder bores 1 a houses each of the
pistons 25 in such a manner that thepistons 25 can reciprocate in the front-rear direction. The front-rear direction is an example of “axial directions” according to the present invention. The front side is an example of “one end side in the axial direction”, and the rear side is an example of “the other side in the axial direction”. - The cylinder block 1 is held between the front housing 3 disposed in front thereof and the
rear housing 5 disposed at the rear thereof, and fastened in this state with a plurality ofbolts 7. In other words, the front housing 3 is fixed to the front of the cylinder block 1, and therear housing 5 is fixed to the rear of the cylinder block 1. The front housing 3 has acrank chamber 9 formed therein. Avalve unit 29 is disposed between therear housing 5 and the cylinder block 1. - The driving means 4 comprises a
drive shaft 11, alug plate 15, aswash plate 17 and alink mechanism 23, for example. - A
shaft hole 3 a is formed in the front housing 3. Ashaft hole 1 b is formed in the cylinder block 1. - The
drive shaft 11 extends in thecrank chamber 9 in the front-rear direction. A front end part of thedrive shaft 11 protrudes to the outside of the front housing 3 through theshaft hole 3 a. In theshaft hole 3 a, ashaft seal device 9 s and abearing device 10 a are fitted. Theshaft seal device 9 s seals the gap between thedrive shaft 11 and the front housing 3. A rear end part of thedrive shaft 11 protrudes into theshaft hole 1 b. A bearingdevice 10 b is provided between theshaft hole 1 b and the rear end part of thedrive shaft 11. Thedrive shaft 11 is rotatably supported in the shaft holes 3 a and 1 b with the bearingdevices - The
lug plate 15 is press-fitted around thedrive shaft 11 in thecrank chamber 9. A bearingdevice 10 c is provided between thelug plate 15 and the front housing 3. - A
pulley 13 is fixed to the front end part of thedrive shaft 11. Abearing device 3 b is disposed between thepulley 13 and the front housing 3. Abelt 13 c, which is driven by an engine or a motor of a vehicle, is wound around thepulley 13. An electromagnetic clutch may be provided instead of thepulley 13. - The
swash plate 17 is penetrated by thedrive shaft 11 in thecrank chamber 9. Theswash plate 17 is positioned behind thelug plate 15. Aninclination reducing spring 19 is provided on the circumference of thedrive shaft 11 between thelug plate 15 and theswash plate 17. In thecrank chamber 9, acirclip 11 a is fixed to thedrive shaft 11, and areturn spring 21 is provided on the circumference of thedrive shaft 11 between thecirclip 11 a and theswash plate 17. - The
link mechanism 23 connects thelug plate 15 and theswash plate 17 to each other in thecrank chamber 9. Thelink mechanism 23 supports theswash plate 17 in such a manner that the inclination angle of theswash plate 17 with respect to thelug plate 15 can be changed. - A front-rear pair of
shoes pistons 25 and theswash plate 17. The pairs ofshoes swash plate 17 into the reciprocation of thecorresponding piston 25 in the front-rear direction. - In each of the cylinder bores 1 a, a rear end surface of each of the
pistons 25 faces thevalve unit 29. With this configuration, thepistons 25 each defines acompression chamber 31 in a rear part of each of the cylinder bores 1 a. Thevalve unit 29 operates to make thecompression chambers 31 suck in a refrigerating gas from asuction chamber 5 a when thepistons 25 are in a suction stroke. Thevalve unit 29 also operates to confine the refrigerating gas in thecompression chambers 31 when the pistons are in a compression stroke, and to make thecompression chambers 31 discharge the refrigerating gas to adischarge chamber 5 b when thepistons 25 are in a discharge stroke. - As shown in
FIGS. 1 and 2 , therear housing 5 has thesuction chamber 5 a, which is radially inwardly positioned, and thedischarge chamber 5 b, which is radially outwardly positioned. Thedischarge chamber 5 b extends in the circumferential direction to annularly surround thesuction chamber 5 a. Therear housing 5 also has aninlet port 5 h through which thesuction chamber 5 a is in communication with the outside. Thesuction chamber 5 a is defined by anannular wall 5 m formed in therear housing 5. Thedischarge chamber 5 b is defined by theannular wall 5 m and an outerperipheral wall 5 n of therear housing 5. - As shown in
FIG. 1 , thecrank chamber 9 and thesuction chamber 5 a are connected to each other by ableed passage 42. Thecrank chamber 9 and thedischarge chamber 5 b are connected to each other bysupply passages rear housing 5 houses avolume control valve 2. Thevolume control valve 2 is provided between thesupply passages - The opening of the
volume control valve 2 is externally adjusted by power supply control, thereby controlling the balance between the amount of the refrigerating gas at high pressure introduced into thecrank chamber 9 from thedischarge chamber 5 b through thesupply passages suction chamber 5 a from thecrank chamber 9 through thebleed passage 42, and determining the internal pressure of thecrank chamber 9. As the internal pressure of thecrank chamber 9 changes, the difference in pressure between thecrank chamber 9 and thecompression chamber 31 changes, the inclination angle of theswash plate 17 changes, and accordingly, the strokes of thepistons 25, that is, the discharge volume of the compressor is adjusted. - An
outlet port 1 h, through which thedischarge chamber 5 b is in communication with the outside, is provided on the outer peripheral. surface of the cylinder block 1. Amuffler 100 is provided between thedischarge chamber 5 b and theoutlet port 1 h. - As shown in
FIGS. 1 to 4 , themuffler 100 has amuffler chamber 110, aninlet channel 101, andoutlet channels - The
rear housing 5 has a closed-endcircular hole 5G that extends rearward from arear wall surface 5 r of thedischarge chamber 5 b. The cylindrical inner wall surface of the closed-endcircular hole 5G is an innerperipheral surface 113. The circular bottom surface of the closed-endcircular hole 5G is asecond end surface 112 positioned at the rear end of the innerperipheral surface 113. A disk-shapedlid member 109 is press-fitted in the closed-endcircular hole 5G. As shown inFIG. 4 , a front surface of thelid member 109 is substantially flush with therear wall surface 5 r. The rear surface of thelid member 109 is afirst end surface 111 positioned at the front end of the innerperipheral surface 113. As shown inFIG. 3 , themuffler chamber 110 is a cylindrical cavity defined by the innerperipheral surface 113, thefirst end surface 111 and thesecond end surface 112. - As shown in
FIGS. 1 and 2 , in therear housing 5, themuffler chamber 110 is positioned between theannular wall 5 m and the outerperipheral wall 5 n. As shown inFIG. 2 , therear housing 5 has a plurality ofbolt insertion holes 6, into which thebolts 7 are inserted. In thedischarge chamber 5 b, themuffler chamber 110 is positioned between twobolt insertion holes FIG. 1 , a distance A from afront end surface 5 f of therear housing 5 to thesecond end surface 112 of themuffler chamber 111 is equal to or smaller than a distance B from thefront end surface 5 f of therear housing 5 to arear end surface 5 e of thedischarge chamber 5 b. - As shown in
FIGS. 2 to 4 , theinlet channel 101 is a circular hole that penetrates thelid member 109 at the center thereof in the front-rear direction. Theinlet channel 101 forms aninlet opening 101 h having a circular shape in thefirst end surface 111. That is, thelid member 109 fitted inside the front part of the innerperipheral surface 113 separates thedischarge chamber 5 b and themuffler chamber 110 from each other and provides thefirst end surface 111, theinlet channel 101 and the inlet opening 101 h. Theinlet channel 101 provides communication between thedischarge chamber 5 b and themuffler chamber 110. - As shown in
FIGS. 1 and 2 , theoutlet channel 102 a is formed in therear housing 5. Theoutlet channel 102 a is a hole that extends straight from apart 5S of the front surface of therear housing 5 positioned radially outward from thedischarge chamber 5 b toward the innerperipheral surface 113. Theoutlet channel 102 a is inclined with respect to the front-rear direction. - As shown in
FIG. 1 , theoutlet channel 102 b is a hole that is formed in thevalve unit 29 and the cylinder block 1 and extends straight in the front-rear direction. A rear end part of theoutlet channel 102 b is in communication with a front end part of theoutlet channel 102 a. A front end part of theoutlet channel 102 b is in communication with theoutlet port 1 h. - As shown in
FIGS. 1 to 4 , theoutlet channel 102 a forms anoutlet opening 102 h having an elliptical shape in the innerperipheral surface 113 at a position spaced apart from thesecond end surface 112. As shown inFIG. 4 , an inner diameter D2 of theoutlet channel 102 a is larger than an inner diameter D1 of theinlet channel 101. - In a vehicle air-conditioning apparatus, the
discharge chamber 5 b of the compressor according to the embodiment 1 configured as described above is connected to a condenser via themuffler chamber 100 and theoutlet port 1 h, the condenser is connected to an evaporator via an expansion valve, and the evaporator is connected to thesuction chamber 5 a via theinlet port 5 h. When an engine or the like rotationally drives thedrive shaft 11, the refrigerating gas is introduced from thesuction chamber 5 a into thecompression chamber 31 in a discharge volume corresponding to the inclination angle of theswash plate 17 and compressed therein, and then discharged into thedischarge chamber 5 b. - In this process, if the opening of the
volume control valve 2 is decreased, the internal pressure of thecrank chamber 9 decreases. As a result, the inclination angle of theswash plate 17 increases, the strokes of thepistons 25 increases, and the discharge volume of the compressor increases. To the contrary, if the opening of thevolume control valve 2 is increased, the internal pressure of thecrank chamber 9 increases. As a result, the inclination angle of theswash plate 17 decreases, the strokes of thepistons 25 decreases, and the discharge volume of the compressor decreases. In this way, the discharge volume of the compressor can be changed as required. - As shown in
FIGS. 3 and 4 , in this compressor, the refrigerating gas at high pressure in thedischarge chamber 5 b flows through theinlet channel 101 into themuffler chamber 110 at the inlet opening 101 h formed in thefirst end surface 111, flows out into theoutlet channels outlet opening 102 h formed in the innerperipheral surface 113, and is discharged to the outside at theoutlet port 1 h. With this compressor, in this process, the flow of the refrigerating gas is narrowed down in theinlet channel 101 and then expands in themuffler chamber 110, so that the discharge pulsation can be reduced. - The
muffler chamber 110 is a cylindrical cavity defined by the cylindrical innerperipheral surface 113, thefirst end surface 111 and thesecond end surface 112. The inventors have found that the amplitude of the pulsation of the pressure of the refrigerating gas flowing into themuffler chamber 110 tends to be smaller in a part close to the innerperipheral surface 113 than in a part close to thesecond end surface 112. Thus, the amplitude of the pulsation of the pressure of the refrigerating gas flowing from themuffler chamber 110 into theoutlet channels outlet opening 102 h can be smaller in the case where theoutlet channel 102 a opens in the innerperipheral surface 113 at a position spaced apart from thesecond end surface 112 than in the case where theoutlet channel 102 a opens in thesecond end surface 112. - With this compressor, since the inner diameter D2 of the
outlet channel 102 a is larger than the inner diameter D1 of theinlet channel 101, the flow of the refrigerating gas introduced from themuffler chamber 110 into theoutlet channel 102 a through theoutlet opening 102 h is less likely to be narrowed down by theoutlet channel 102 a. Therefore, the small amplitude of the pulsation of the pressure of the refrigerating gas can be appropriately maintained until the refrigerating gas reaches theoutlet port 1 h. - As described above, the compressor can reduce the discharge pulsation and can accordingly reduce the volume of the
muffler chamber 110. As a result, themuffler 100 disposed in therear housing 5 of this compressor can be less bulky. In addition, since themuffler chamber 110 is positioned between theannular wall 5 m and the outerperipheral wall 5 n, themuffler 100 can be prevented from protruding in the radially outward direction of therear housing 5. In addition, since the distance A from thefront end surface 5 f of therear housing 5 to thesecond end surface 112 of themuffler chamber 110 is set to be equal to or smaller than the distance B from thefront end surface 5 f of therear housing 5 to therear end surface 5 e of thedischarge chamber 5 b, themuffler 100 can be prevented from protruding in the axial direction of therear housing 5. - Owing to these characteristics, the compressor according to the embodiment 1 can have a reduced size and appropriately reduce the discharge pulsation.
- In addition, with this compressor, the inner
peripheral surface 113 and thesecond end surface 112 can be easily formed by forming the closed-endcircular hole 5G, which is recessed toward the rear from thedischarge chamber 5 b, in therear housing 5. In addition, with this compressor, theoutlet channel 102 a and theoutlet opening 102 h can be easily formed by forming a hole that obliquely penetrates therear housing 5 from thepart 5S of the front surface of therear housing 5 to the innerperipheral surface 113 of themuffler chamber 110. In addition, thefirst end surface 111, theinlet channel 101 and the inlet opening 101 h can be easily formed by fitting the disk-shapedlid member 109 having an opening formed therein inside the innerperipheral surface 113. Owing to these characteristics, the compressor can be manufactured at low cost. - As shown in
FIGS. 5 and 6 , a compressor according to anembodiment 2 differs from the compressor according to the embodiment 1 in that themuffler 100 is additionally provided with anintermediate member 230. The remainder of the configuration of the compressor according to theembodiment 2 is the same as that according to the embodiment 1. The same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted. - The
intermediate member 230 is fitted inside the innerperipheral surface 113 between thefirst end surface 111 and thesecond end surface 112. Theintermediate member 230 comprises amain body part 232 and anextension part 231. - The
main body part 232 is disk-shaped, and the outer peripheral edge thereof is partially radially inwardly recessed to form a recessedpart 232 a. Theextension part 231 is integral with themain body part 232. Theextension part 231 encloses the recessedpart 232 a and extends toward the front. Aperipheral edge 231 e of theextension part 231 is in intimate contact with the innerperipheral surface 113. - The
main body part 232 and theextension part 231 of theintermediate member 230 divide themuffler chamber 110 into afirst muffler chamber 210 a positioned to the front and asecond muffler chamber 210 b positioned to the rear. - In the
intermediate member 230, afirst opening 231 h, asecond opening 232 h, and anintermediate flow channel 233 are formed. Thefirst opening 231 h is a circular hole formed in a front part of theextension part 231. Thefirst opening 231 h penetrates theextension part 231 in the radial direction and opens into thefirst muffler chamber 210 a. Thesecond opening 232 h is a clearance formed in a rear surface of themain body part 232 between the recessedpart 232 a and the innerperipheral surface 113, and opens into thesecond muffler chamber 210 b. Theintermediate flow channel 233 is a cavity formed between theextension part 231 and themain body part 232 of theintermediate member 230 and the innerperipheral surface 113, andintermediate flow channel 233 extends in the front-rear direction. Theextension part 231 is in communication with thefirst opening 231 h at the front thereof and is in communication with thesecond opening 232 h at the rear thereof. - The
first opening 231 h is formed in the front part of theextension part 231 so as to penetrate theextension part 231 in the radial direction. Alternatively, however, thefirst opening 231 h may be formed in the front part of theextension part 231 at a position opposed to thefirst end surface 111 so as to penetrate theextension part 231 in the axial direction. - As shown in
FIG. 5 , an inner diameter D3 of thefirst opening 231 h is smaller than the inner diameter D2 of theoutlet channel 102 a. The inner diameter D3 of thefirst opening 231 h is slightly larger than the inner diameter D1 of theinlet channel 101. - With the compressor according to the
embodiment 2 configured as described above, the refrigerating gas at high pressure in thedischarge chamber 5 b flows into thefirst muffler chamber 210 a through theinlet channel 101 at the inlet opening 101 h, and then flows into thesecond muffler chamber 210 b through thefirst opening 231 h, theintermediate flow channel 233 and thesecond opening 232 h. The refrigerating gas then flows out into theoutlet channels outlet opening 102 h and is discharged to the outside through theoutlet port 1 h. In this process, this compressor can further reduce the discharge pulsation, because the flow of the refrigerating gas is once narrowed down by theinlet channel 101 and then expanded in thefirst muffler chamber 210 a, and then narrowed down again by theintermediate flow channel 233 and then expanded in thesecond muffler chamber 210 b. - In addition, in this compressor, the
first muffler chamber 210 a is a substantially cylindrical cavity defined by the cylindrical innerperipheral surface 113, thefirst end surface 111 positioned to the front, themain body part 232 positioned to the rear of thefirst end surface 111, and theextension part 231 that is integral with themain body part 232 and extends toward the front. The amplitude of the pulsation of the pressure of the refrigerating gas flowing into thefirst muffler chamber 210 a tends to be smaller in a part close to the front of theextension part 231 than in a part close to themain body part 232. Thus, the amplitude of the pulsation of the pressure of the refrigerating gas flowing into thesecond muffler chamber 210 b through thefirst opening 231 h, theintermediate flow channel 233 and thesecond opening 232 h can be smaller in the case where the first opening. 231 h opens in the front part of theextension part 231 than in the case where thefirst opening 231 h opens in themain body part 232. - The
second muffler chamber 210 b is a cylindrical cavity defined by the cylindrical innerperipheral surface 113, thesecond end surface 112 positioned to the rear, and themain body part 232 positioned to the front of thesecond end surface 112. The amplitude of the pulsation of the pressure of the refrigerating gas flowing from thefirst muffler chamber 210 a into thesecond muffler chamber 210 b through thefirst opening 231 h, theintermediate flow channel 233 and thesecond opening 232 h tends to be smaller in a part close to the innerperipheral surface 113 than in a part close to thesecond end surface 112. Thus, the amplitude of the pulsation of the pressure of the refrigerating gas flowing out of thesecond muffler chamber 210 b into theoutlet channels flow channel 102 a has theoutlet opening 102 h in the innerperipheral surface 113 than in the case where theoutlet channel 102 a opens in thesecond end surface 112. - Owing to these characteristics, the compressor according to the
embodiment 2 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressor according to the embodiment 1. - As shown in
FIGS. 7 and 8 , a compressor according to an embodiment 3 differs from the compressor according to the embodiment 1 in that themuffler 100 is additionally provided with threeintermediate members 330. The remainder of the configuration of the compressor according to the embodiment 3 is the same as that according to the embodiment 1. The same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted. - The three
intermediate members 330 are disk-shaped members having the same shape. Eachintermediate member 330 is fitted inside the innerperipheral surface 113 side by side in the front-rear direction between thefirst end surface 111 and thesecond end surface 2. Theintermediate members 330 divide themuffler chamber 110 into fourmuffler chamber sections intermediate members 330, each muffler chamber section 310 a-310 c positioned to the front of thatintermediate member 330 is an example of the “first muffler chamber” according to the present invention, and eachmuffler chamber section 310 b-310 d positioned to the rear of thatintermediate member 330 is an example of the “second muffler chamber” according to the present invention. - A plurality of sets of a
first opening 331, asecond opening 332 and anintermediate flow channel 333 are formed in eachintermediate member 330. Thefirst opening 331, thesecond opening 332 and theintermediate flow channel 333 are parts of a perforated substantially funnel-shaped part protruding toward the front formed by piercing theintermediate member 330 with a sharp-pointed needle-like tool. Thefirst opening 331 opens into the muffler chamber section 310 a-310 c positioned to the front. Thesecond opening 332 opens into themuffler chamber section 310 b-310 d positioned to the rear. Theintermediate flow channel 333 provides communication between thefirst opening 331 and thesecond opening 332. - As shown in
FIG. 7 , when viewed in the front-rear direction, the sets of thefirst opening 331, thesecond opening 332 and theintermediate flow channel 333 formed in one of adjacent twointermediate members 330 are displaced from the sets of thefirst opening 331, thesecond opening 332 and theintermediate flow channel 333 formed in the other of the adjacent twointermediate members 330. - With the compressor according to the embodiment 3 configured as described above, the refrigerating gas flowing into the
muffler chamber 110 sequentially passes through themuffler chamber sections 310 a to 310 d. In this process, the flow of the refrigerating gas is narrowed down by the set of thefirst opening 331, thesecond opening 332 and theintermediate flow channel 333 formed in eachintermediate member 330 and then expands. In addition, the refrigerating gas is agitated as the refrigerating gas flows in a serpentine path since the sets of thefirst opening 331, thesecond opening 332 and theintermediate flow channel 333 are displaced from each other when viewed in the front-rear direction. As a result, the amplitude of the pulsation of the pressure of the refrigerating gas is reduced. - Owing to these characteristics, the compressor according to the embodiment 3 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressors according to the
embodiments 1 and 2. - As shown in
FIGS. 9 and 10 , a compressor according to anembodiment 4 differs from the compressor according to the embodiment 1 in that themuffler 100 is additionally provided with an agitatingmember 440. The remainder of the configuration of the compressor according to theembodiment 4 is the same as that according to the embodiment 1. The same components as those in the embodiment 1 will be denoted by the same reference numerals as those in the embodiment 1, and descriptions thereof will be simplified or omitted. - The agitating
member 440 is inserted in themuffler chamber 110. The agitatingmember 440 has a plurality of minute reflectingsurface elements 441 whose reflecting surfaces intersect with the front-rear direction. The reflectingsurface elements 441 are dispersed in themuffler chamber 110 by fixing the reflectingsurface elements 441 onto a wire coil (not shown) at intervals and placing the coil wire in themuffler chamber 110, for example. Alternatively, the reflectingsurface elements 441 may be parts of a stainless steel scourer made of spiral-shaped chips produced in lathe machining of a stainless steel material, for example. - With the compressor according to the
embodiment 4 configured as described above, the refrigerating gas flowing into themuffler chamber 110 is agitated by the plurality of minute reflectingsurface elements 441 of the agitatingmember 440, so that the amplitude of the pulsation of the pressure of the refrigerating gas is reduced. - Owing to these characteristics, the compressor according to the
embodiment 4 can have a reduced size and appropriately reduce the discharge pulsation, as with the compressors according to the embodiments 1 to 3. - Although the embodiments 1 to 4 of the present invention have been described above, of course, the present invention is not limited to the embodiments 1 to 4, and various changes can be made to the embodiments as required without departing from the spirit of the present invention.
- For example, in the embodiments 1 to 4, the
outlet opening 102 h is formed in the innerperipheral surface 113 at a position that is spaced apart from thesecond end surface 112 toward thefirst end surface 111 and is closer to thesecond end surface 112 than thefirst end surface 111. Alternatively, however, theoutlet opening 102 h may be formed in the innerperipheral surface 113 at a position that is spaced apart from thesecond end surface 112 toward thefirst end surface 111 and is closer to thefirst end surface 111 than thesecond end surface 112. - Furthermore, in the embodiments 1 to 4, the inner diameter D2 of the
outlet channel 102 a is larger than the inner diameter D1 of theinlet channel 101. Alternatively, however, the inner diameter D2 may be smaller than or equal to the inner diameter D1. - Furthermore, in the. embodiments 1 to 4, the distance A from the
front end surface 5 f of therear housing 5 to thesecond end surface 112 of themuffler chamber 110 is equal to or smaller than the distance B from thefront end surface 5 f of therear housing 5 to the rear end surface. 5 e of thedischarge chamber 5 b. Alternatively, however, themuffler chamber 110 may be configured so that the distance A is longer than the distance B.
Claims (8)
1. A variable displacement compressor with single-head pistons, comprising:
a cylinder block having a plurality of cylinder bores that are formed side by side in a circumferential direction and extend in parallel with each other in an axial direction;
a front housing that is fixed to one end side of the cylinder block in the axial direction and has a crank chamber formed therein;
a rear housing that is fixed to the other end side of the cylinder block in the axial direction and has a suction chamber and a discharge chamber formed therein;
a plurality of pistons each housed in each of the cylinder bores so as to reciprocate and defining a compression chamber in each of the cylinder bores on the other end side; and
driving means that is provided in the crank chamber and is capable of making each of the pistons reciprocate and changing strokes of each of the pistons,
the rear housing having an annular wall that separates the suction chamber and the discharge chamber from each other,
the discharge chamber being formed between the annular wall and an outer peripheral wall of the rear housing so as to extend in the circumferential direction and annularly surround the suction chamber,
an outlet port, through which the discharge chamber is in communication with the outside, being formed in the cylinder block or the rear housing,
a muffler being provided between the discharge chamber and the outlet port,
the muffler having a muffler chamber, an inlet channel and an outlet channel, and
the muffler chamber being formed in the rear housing, the inlet channel providing communication between the discharge chamber and the muffler chamber, and the outlet channel providing communication between the muffler chamber and the outlet port,
wherein the muffler chamber has:
a first end surface positioned on the one end side of the muffler chamber;
a second end surface positioned on the other end side of the muffler chamber; and
an inner peripheral surface having a cylindrical shape that is positioned between the first end surface and the second end surface and extends from the discharge chamber toward the other end side,
the muffler chamber is positioned between the annular wall and the outer peripheral wall,
the inlet channel opens in the first end surface, and
the outlet channel opens in the inner peripheral surface at a position spaced apart from the second end surface.
2. The variable displacement compressor with single-head pistons according to claim 1 , wherein the inner peripheral surface, the second end surface and the outlet channel are formed in the rear housing,
the first end surface is formed by a disk-shaped lid member that is fitted inside the inner peripheral surface and separates the discharge chamber and the muffler chamber from each other, and
the inlet channel is formed in the lid member.
3. The variable displacement compressor with single-head pistons according to claim 2 , wherein the inner peripheral surface and the second end surface forma closed-end circular hole that is recessed in the discharge chamber toward the other end side, and
the outlet channel is a straight hole that penetrates the rear housing from the one end side to the inner peripheral surface.
4. The variable displacement compressor with single-head pistons according to claim 1 , wherein an inner diameter of the outlet channel is larger than an inner diameter of the inlet channel.
5. The variable displacement compressor with single-head pistons according to claims 1 , wherein an intermediate member is fitted inside the inner peripheral surface, the intermediate member dividing the muffler chamber into a first muffler chamber positioned on the one end side and a second muffler chamber positioned on the other end side,
a first opening, a second opening and an intermediate flow channel are formed in the. intermediate member, and
the first opening opens into the first muffler chamber, the second opening opens into the second muffler chamber, and the intermediate flow channel provides communication between the first opening and the second opening.
6. The variable displacement compressor with single-head pistons according to claim 5 , wherein the intermediate member includes a disk-shaped main body part and an extension part that is integral with the main body part and extends toward the one end side,
the first opening is formed in the extension part at a position on the one end side,
the second opening is formed in the main body part at a position on the other end side, and
the intermediate flow channel is formed between the extension part and the main body part of the intermediate member and the inner peripheral surface.
7. The variable displacement compressor with single-head pistons according to claim 5 , wherein a plurality of the intermediate members arranged side by side in the axial direction are fitted inside the inner peripheral surface, and
the first opening, the second opening and the intermediate flow channel formed in one of adjacent two of the intermediate members are displaced from the first opening, the second opening and the intermediate flow channel formed in the other of the adjacent two of the intermediate members when viewed in the axial direction.
8. The variable displacement compressor with single-head pistons according to claim 1 , wherein an agitating member is inserted in the muffler chamber, the agitating member having a plurality of reflecting surface elements whose reflecting surfaces intersect with the axial direction.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-149005 | 2013-07-18 | ||
JP2013149005 | 2013-07-18 | ||
JP2014006566A JP5920367B2 (en) | 2013-07-18 | 2014-01-17 | Single-head piston variable displacement compressor |
JP2014-006566 | 2014-01-17 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150023812A1 true US20150023812A1 (en) | 2015-01-22 |
Family
ID=51205266
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/327,863 Abandoned US20150023812A1 (en) | 2013-07-18 | 2014-07-10 | Variable displacement compressor with single-head pistons |
Country Status (6)
Country | Link |
---|---|
US (1) | US20150023812A1 (en) |
EP (1) | EP2826995A3 (en) |
JP (1) | JP5920367B2 (en) |
KR (1) | KR20150010604A (en) |
CN (1) | CN104295466A (en) |
BR (1) | BR102014017590A2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN111326137A (en) * | 2018-12-13 | 2020-06-23 | 允匠智能科技(上海)有限公司 | Voice robot interaction system based on office intelligence |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2002250279A (en) * | 2001-02-21 | 2002-09-06 | Zexel Valeo Climate Control Corp | Compressor |
US20090136366A1 (en) * | 2005-10-28 | 2009-05-28 | Sanden Corporation | Compressor |
US20100018386A1 (en) * | 2006-03-29 | 2010-01-28 | Kabushiki Kaisha Toyota Jidoshokki | Compressor |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN2192725Y (en) * | 1994-06-01 | 1995-03-22 | 菅宝贵 | Muffler |
JPH09287564A (en) * | 1996-04-23 | 1997-11-04 | Zexel Corp | Reciprocating compressor |
KR19990023220U (en) * | 1997-12-01 | 1999-07-05 | 배길훈 | Swash plate compressor |
JP3509560B2 (en) * | 1998-06-15 | 2004-03-22 | 株式会社豊田自動織機 | Oil separation structure of compressor |
US6705843B1 (en) * | 2002-10-17 | 2004-03-16 | Visteon Global Technologies, Inc. | NVH and gas pulsation reduction in AC compressor |
JP4888803B2 (en) * | 2005-07-04 | 2012-02-29 | 株式会社ヴァレオジャパン | Compressor |
JP2009293386A (en) * | 2008-06-02 | 2009-12-17 | Toyota Industries Corp | Compressor |
CN101581243A (en) * | 2009-06-15 | 2009-11-18 | 无锡红湖消声器有限公司 | Diffuse reflection muffler |
KR101212909B1 (en) * | 2010-05-24 | 2012-12-14 | 한라공조주식회사 | Variable displacement swash plate type compressor |
JP5592840B2 (en) * | 2011-06-16 | 2014-09-17 | サンデン株式会社 | Compressor |
-
2014
- 2014-01-17 JP JP2014006566A patent/JP5920367B2/en active Active
- 2014-07-10 US US14/327,863 patent/US20150023812A1/en not_active Abandoned
- 2014-07-14 KR KR1020140088224A patent/KR20150010604A/en not_active Application Discontinuation
- 2014-07-16 EP EP14177203.8A patent/EP2826995A3/en not_active Withdrawn
- 2014-07-17 CN CN201410340608.9A patent/CN104295466A/en active Pending
- 2014-07-17 BR BR102014017590A patent/BR102014017590A2/en not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002250279A (en) * | 2001-02-21 | 2002-09-06 | Zexel Valeo Climate Control Corp | Compressor |
US20090136366A1 (en) * | 2005-10-28 | 2009-05-28 | Sanden Corporation | Compressor |
US20100018386A1 (en) * | 2006-03-29 | 2010-01-28 | Kabushiki Kaisha Toyota Jidoshokki | Compressor |
Also Published As
Publication number | Publication date |
---|---|
EP2826995A3 (en) | 2015-09-02 |
BR102014017590A2 (en) | 2015-10-06 |
EP2826995A2 (en) | 2015-01-21 |
CN104295466A (en) | 2015-01-21 |
JP2015038344A (en) | 2015-02-26 |
JP5920367B2 (en) | 2016-05-18 |
KR20150010604A (en) | 2015-01-28 |
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