US20150252797A1 - Variable-Capacity Compressor - Google Patents
Variable-Capacity Compressor Download PDFInfo
- Publication number
- US20150252797A1 US20150252797A1 US14/441,451 US201314441451A US2015252797A1 US 20150252797 A1 US20150252797 A1 US 20150252797A1 US 201314441451 A US201314441451 A US 201314441451A US 2015252797 A1 US2015252797 A1 US 2015252797A1
- Authority
- US
- United States
- Prior art keywords
- passage
- suction
- chamber
- space
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/109—Lubrication
-
- 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
- F04B27/0804—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 rotary cylinder block
-
- 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
- F04B27/14—Control
-
- 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
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- 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
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
-
- 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
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
Definitions
- the present invention relates to a variable-displacement compressor, and more specifically, relates to a variable-displacement compressor that varies a discharge displacement of a refrigerant gas by controlling a pressure in a crank chamber by a control valve depending on a pressure in a suction chamber.
- Patent Document 1 discloses this type of a variable-displacement compressor.
- a control valve is provided in a communication passage communicating between a discharge chamber and a crank chamber on a back side of a piston.
- the control valve controls a pressure in the crank chamber by controlling an opening of the communication passage depending on a pressure in a suction chamber, and a stroke of the piston is changed. Accordingly, a discharge displacement of a refrigerant gas is varied.
- the suction chamber is connected to the control valve by a pressure introducing passage, and a pressure in the suction chamber is introduced to the control valve.
- the control valve controls an opening of the communication passage by detecting a change in a pressure in the suction chamber, an amount of a high pressure refrigerant gas to be introduced to the crank chamber is increased or decreased, and a stroke of the piston is changed by changing an inclination (angle of inclination) of a swash plate. Accordingly, a discharge displacement of a refrigerant gas is increased or decreased.
- Patent Document 1 Japanese Patent Application Laid-open Publication No. 2012-127233
- variable-displacement compressor In such a variable-displacement compressor, a lubricating oil is mixed in a refrigerant gas to lubricate each component of the compressor. Therefore, in a configuration like a conventional variable-displacement compressor, in which a refrigerant gas including a lubricating oil to be returned from a suction passage to a suction chamber via an external refrigerant circuit after being discharged from the compressor is directly introduced to a control valve from a pressure introducing passage, sensitivity of the control valve might be lowered since the lubricating oil flows into the control valve especially in a case in which a large amount of the oil is circulating.
- the present invention is focused on the above issue and seeks to provide a variable-displacement compressor that can control an amount of a lubricating oil flowing into a control valve and prevent sensitivity reduction of the control valve caused by inflow of the lubricating oil.
- a variable-displacement compressor includes: a piston that compresses a refrigerant gas drawn from a suction chamber via a suction hole and discharges the refrigerant gas to a discharge chamber via a discharge hole; a first passage that communicates between a crank chamber on a back side of the piston and the discharge chamber; a control valve provided in the first passage and that controls an opening of the first passage; a second passage that communicates between the crank chamber and the suction chamber, and that is provided with an orifice; and a pressure introducing passage configured to introduce a pressure in the suction chamber to the control valve.
- the control valve controls an opening of the first passage depending on the pressure in the suction chamber, which has been introduced from the pressure introducing passage, so as to control a pressure in the crank chamber, so that a stroke of the piston is changed, and accordingly, a discharge displacement of a refrigerant gas is varied.
- the suction chamber includes a storage area for separating a lubricating oil from a refrigerant gas inflowing from a suction passage and for storing the lubricating oil, and the pressure introducing passage is open to an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows, so as to introduce the pressure in the suction chamber to the control valve.
- the suction chamber includes the storage area for storing the lubricating oil separated from the refrigerant gas inflowed from the suction passage, and the pressure introducing passage is open to an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows. Therefore, an amount of the lubricating oil in the refrigerant gas flowing into the control valve via the pressure introducing passage can be reduced, and sensitivity reduction of the control valve caused by inflow of the lubricating oil can be prevented.
- FIG. 1 is a cross-sectional view illustrating an embodiment of a variable-displacement compressor according to the present invention.
- FIG. 2 is a cross-sectional view of a control valve applied to the embodiment.
- FIG. 3 is a view illustrating a valve plate viewed from a cylinder block side, according to the embodiment.
- FIG. 4 is a view illustrating a discharge valve forming body viewed from a cylinder block side, according to the embodiment.
- FIG. 5 is a view illustrating a cylinder head viewed from a cylinder block side, according to the embodiment.
- FIG. 6 is a view illustrating a head gasket viewed from a cylinder block side, according to the embodiment.
- FIG. 7 is a cross-sectional view taken along with a line A-O-A viewed from arrows A, in a state in which the head gasket illustrated in FIG. 6 is assembled.
- FIG. 8 is a cross-sectional view taken along with a line viewed from arrows B, illustrated in FIG. 6 .
- FIG. 9 is a cross-sectional view taken along with a line viewed from arrows C, in a state in which the cylinder head illustrated in FIG. 5 is assembled.
- FIG. 1 illustrates a schematic configuration of a variable-displacement compressor according to a first embodiment of the present invention
- FIG. 1 is an example of a clutch-less variable-displacement compressor for use in a vehicle air conditioning system.
- a variable-displacement compressor 100 includes: a cylinder block 101 in which multiple cylinder bores 101 a are formed; a front housing 102 provided at one end of the cylinder block 101 ; and a cylinder head 104 provided at another end of the cylinder block 101 via a valve plate 103 .
- a drive shaft 110 is provided so as to cross in a crank chamber 140 formed by the cylinder block 101 and the front housing 102 .
- a swash plate 111 is arranged around an intermediate portion in an axial direction of the drive shaft 110 .
- the swash plate 111 is connected to a rotor 112 , which is fixed to the drive shaft 110 , via a linkage 120 , and is supported so that an inclination thereof can be varied by the drive shaft 110 .
- the linkage 120 includes: a first arm 112 a arranged so as to protrude from the rotor 112 ; a second arm 111 a arranged so as to protrude from the swash plate 111 ; and a link arm 121 rotatably connected at one end to the first arm 112 a via a first connection pin 122 , and rotatably connected at the other end to the second arm 111 a via the second connection pin 123 .
- a through hole 111 b of the swash plate 111 is formed so as to be inclined within a range of the maximum inclination ( ⁇ max) to the minimum inclination ( ⁇ min).
- a minimum-inclination restricting portion coming into contact with the drive shaft 110 is formed to the through hole 111 b.
- the minimum inclination restricting portion of the through hole 111 b allows the swash plate 111 to be inclined to approximately 0°.
- the maximum inclination of the swash plate 111 is restricted when the swash plate 111 comes into contact with the rotor 112 .
- a disinclining spring 114 for biasing the swash plate 111 toward the minimum inclination is mounted around the drive shaft 110 between the rotor 112 and the swash plate 111 .
- an inclining spring 115 for biasing the swash plate 11 in a direction increasing an inclination of the swash plate 111 is mounted around the drive shaft 110 between the swash plate 111 and a spring support member 116 provided to the drive shaft 110 .
- a biasing force of the inclining spring 115 at the minimum inclination is set to be greater than that of the disinclining spring 114 .
- One end of the drive shaft 110 is extended to an outer side of the front housing 102 , passing through a boss portion 102 a of the front housing 102 , and connected to a power transmission device (not illustrated).
- a shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102 a to block the inside of the crank chamber 140 from the outside.
- the connected body of the drive shaft 110 and the rotor 112 is supported by bearings 131 and 132 in a radial direction and supported by a bearing 133 and a thrust plate 134 in a thrust direction.
- a gap between the thrust plate 134 of the drive shaft 110 and a portion coming into contact with the thrust plate 134 is adjusted to a predetermined gap by an adjusting screw 135 .
- Power from an external driving source is transmitted to a power transmission device, and the drive shaft 110 rotates in synchronization with the power transmission device.
- a piston 136 is arranged in the cylinder bore 101 a.
- An outer periphery of the swash plate 111 is accommodated in an internal space of an end portion of the piston 136 protruding toward the crank chamber 140 .
- the swash plate 111 is synchronized with the piston 136 via a pair of shoes 137 . Therefore, the piston 136 reciprocates in the cylinder bore 101 a by rotation of the swash plate 111 .
- a suction chamber 141 defined by an annular partition wall 104 b is formed at a center thereof, and a discharge chamber 142 defined by the partition wall 104 b and an external wall is formed so that the discharge chamber 142 circularly surrounds the suction chamber 141 .
- the suction chamber 141 is communicated with the cylinder bore 101 a via a suction hole 103 a formed in the valve plate 103 and a suction valve (not illustrated) formed in a suction valve forming body.
- the discharge chamber 142 is communicated with the cylinder bore 101 a via a discharge hole 103 b formed in the valve plate 103 and a discharge valve 138 a formed in a discharge valve forming body 138 , illustrated in FIG. 4 .
- a compressor housing is formed by fixing, with multiple through bolts 105 , the front housing 102 , a center gasket (not illustrated), the cylinder block 101 , a cylinder gasket (not illustrated), the suction valve forming body (not illustrated), the valve plate 103 illustrated in FIG. 3 , the discharge valve forming body 138 illustrated in FIG. 4 , a head gasket 139 illustrated in FIG. 6 , and the cylinder head 104 illustrated in FIG. 5 .
- a suction passage 104 a is formed to communicate between a low pressure side refrigerant circuit (suction side refrigerant circuit) of a vehicle air conditioning system (refrigerant device) and the suction chamber 141 . Accordingly, the suction chamber 141 is connected to the low pressure side refrigerant circuit of the refrigerant device.
- the suction passage 104 a is linearly extended so as to cross a part of the discharge chamber 142 toward the suction chamber 141 from the outside of the cylinder head 104 .
- the suction chamber 141 is partitioned into a first space 141 a connected to the suction passage 104 a and a second space 141 b connected to the suction hole 103 a by a partition member 150 integrally formed with the head gasket 139 .
- the first space 141 a and the second space 141 b are communicated by a communication hole 150 a (illustrated in FIG. 6 ) formed in the partition member 150 as a communication passage.
- the first space 141 a is configured to allow a low pressure refrigerant gas to flow into the first space 141 a from a low pressure side refrigerant circuit via the suction passage 104 a, and the first space 141 a is configured to separate a lubricating oil mixed in the refrigerant gas and to store the separated lubricating oil at a lower side thereof in a gravity direction (bottom portion of the space). Therefore, the first space 141 a corresponds to a storage area according to the present invention.
- the second space 141 b is configured to introduce a refrigerant gas, which has flowed into the second space 141 b through the communication hole 150 a from the first space 141 a and separated from a lubricating oil, to the suction hole 103 a. Therefore, the second space 141 b corresponds to an inflow area according to the present invention.
- the partition member 150 will be described in detail below.
- a muffler 160 for reducing noise and vibration caused by refrigerant pulsation is provided on the cylinder block 101 at an upper portion thereof.
- the muffler 160 is formed by fixing a lid member 106 with a bolt via a sealing member (not illustrated) to a forming wall 101 b divisionally formed at the upper portion of the cylinder block 101 .
- a check valve 200 is arranged in a muffler space 143 in the muffler 160 , to reduce a backward flow of a refrigerant gas from a discharge side refrigerant circuit to the discharge chamber 142 .
- the check valve 200 is arranged at a connecting portion between a communication passage 144 and the muffler space 143 , the communication passage 144 extending across the cylinder head 104 , the valve plate 103 , and the cylinder block 101 and communicating with the discharge chamber 142 .
- the check valve 200 operates in response to a pressure difference between the communication passage 144 (upstream side) and the muffler space 143 (downstream side). When the pressure difference is less than a predetermined value, the check valve 200 blocks the communication passage 144 . When the pressure difference is greater than the predetermined value, the check valve 200 opens the communication passage 144 .
- the discharge chamber 142 is connected to a discharge side refrigerant circuit of a vehicle air conditioning system via a discharge passage including the communication passage 144 , the check valve 200 , the muffler space 143 , and a discharge port 106 a.
- a control valve 300 is provided in the cylinder head 104 .
- the control valve 300 is provided in a pressure supply passage 145 provided as a first passage that communicates between the discharge chamber 142 and the crank chamber 140 on a back side of the piston 136 .
- the control valve 300 adjusts an opening of the pressure supply passage 145 and controls an amount of the discharge refrigerant gas to be introduced to the crank chamber 140 .
- a refrigerant in the crank chamber 140 flows to the second space 141 b of the suction chamber 141 via a pressure releasing passage 146 provided as a second passage that passes through the communication passage 101 c, a space 101 d, an orifice 103 c formed in the valve plate 103 illustrated in FIG. 3 , and a communication hole 138 b formed in the discharge valve forming body 138 illustrated in FIG. 4 .
- control valve 300 changes the pressure in the crank chamber 140 , which in turn changes the inclination of the swash plate 111 , that is, a stroke of the piston 136 .
- a discharge displacement of the variable-displacement compressor 100 can be varied.
- the orifice 103 c is a fixed orifice in the embodiment, the orifice 103 c may be a variable orifice.
- the control valve 300 is a control valve that operates in response to an external electrical signal.
- FIG. 2 illustrates a configuration thereof.
- the control valve 300 includes: a first pressure-sensitive chamber 302 that is formed in a valve housing 301 and communicates with the crank chamber 140 by the pressure supply passage 145 on the crank chamber 140 side via a communication hole 301 a; a valve chamber 303 that communicates with the discharge chamber 142 by the pressure supply passage 145 on the discharge chamber 142 side via a communication hole 301 b; a valve hole 301 c that is open at one end thereof to the first pressure-sensitive chamber 302 and is open at the other end thereof to the valve chamber 303 ; a valve body 304 , one end of which is arranged in the valve chamber 303 and opens and closes the valve hole 301 c, the valve body 304 being slidably supported by a support hole 301 d formed in the valve housing 301 ; a bellows assembly 305 that is provided with a spring in an evacuated inside thereof, and is arranged in the first pressure-sensitive chamber 302 , the bellows assembly 305 receiving a pressure in the crank chamber 140 ;
- three O rings 313 a to 313 c are arranged at an outer periphery of the control valve 300 .
- a receiving space of the control valve 300 formed in the cylinder head 104 is partitioned into an area in which a pressure in the crank chamber 140 is applied, an area in which a pressure in the discharge chamber 142 is applied, and an area in which a pressure in the suction chamber 141 is applied.
- a force acting on the valve body 304 is represented by the following formula (1):
- Ps denotes a pressure in the suction chamber 141 (second space 141 b )
- F(i) denotes an electromagnetic force
- f denotes a biasing force of the spring 310
- F denotes a biasing force of the bellows assembly 305 .
- the control valve 300 adjusts an opening of the pressure supply passage 145 communicating between the discharge chamber 142 and the crank chamber 140 so that a pressure Ps in the suction chamber 141 (second space 141 b ), which has been introduced via the pressure introducing passage 147 , is maintained to a predetermined value determined based on a current flowing to an electromagnetic coil 313 in response to an external signal, to thereby control an amount of a discharge refrigerant gas to be introduced to the crank chamber 140 , to control a discharge displacement of the variable-displacement compressor 100 .
- the pressure Ps in the suction chamber 141 (second space 141 b ) can be varied from the outside by adjusting a current flowing to the electromagnetic coil 313 .
- a discharge displacement is variably controlled so that a pressure in the suction chamber 141 (second space 141 b ) becomes a predetermined value and a pressure in the suction chamber 141 is appropriately controlled in response to the external environment.
- the control valve 300 in the embodiment operates in response to an external signal, a mechanical control valve that operates by sensing a pressure in a suction chamber may be used.
- the partition member 150 is integrally formed by making a center of the head gasket 139 illustrated in FIG. 6 , i.e., a portion facing the suction chamber 141 at a center of the cylinder head 104 , protrude toward the suction chamber 141 by stamping.
- the suction chamber 141 is partitioned into the first space 141 a to which the suction passage 104 a is connected, and the second space 141 b to which the suction hole 103 a is connected.
- a retainer 139 a for restricting an opening of the discharge valve 138 a is formed in an area corresponding to the discharge chamber 142 .
- the head gasket 139 is a rubber-coated metal thin plate. Therefore, the partition member 150 integrally formed with the head gasket 139 is also rubber-coated.
- the second space 141 b partitioned by the partition member 150 includes, as illustrated in FIG. 7 , a central space 141 b 1 and guide passages 141 b 2 radially extended toward the suction holes 103 a from the central space 141 b 1 .
- the guide passage 141 b 2 includes a bottom wall 150 b and side walls 150 c as illustrated in FIG. 8 . As illustrated in FIG.
- the guide passage 141 b 2 includes an area in which the bottom wall 150 b is inclined so that a passage sectional area is reduced toward each of the suction holes 103 a, which are formed in the valve plate 103 to be annularly arranged at approximately equal intervals around an axis O of the drive shaft 110 at an approximately equal distance from the axis O of the drive shaft 110 .
- two communication holes 150 a that communicate between the first space 141 a and the second space 141 b are formed to be open to two guide passages 141 b 2 as illustrated in FIG. 6 .
- the communication hole 150 a is formed by adjusting the position thereof so that a predetermined amount of a lubricating oil can be stored in the first space 141 a.
- the communication hole 150 a is open to a position that is above the axis O of the drive shaft 110 in a gravity direction and outside an area on an extension of the suction passage 104 a into the suction chamber 141 , in order to prevent a main flow of a suction refrigerant, which has flowed into the first space 141 a from the suction passage 104 a, from directly flowing into the communication hole 150 a.
- an orifice 150 d that communicates between the first space 141 a and the second space 141 b is formed in the bottom wall 150 b of the guide passage 141 b 2 positioned below the axis O of the drive shaft 110 in a gravity direction.
- An upper side in FIGS. 3 to 6 is an upper side in a gravity direction.
- the first space 141 a acts as an oil storage chamber for storing a lubricating oil returned from an air conditioning system with an inflow refrigerant gas.
- An opening area of the orifice 150 d is set so that an appropriate amount of a lubricating oil is stored in the first space 141 a.
- the orifice 150 d acts as an oil return passage, which gradually returns a lubricating oil stored in the first space 141 a to the second space 141 b. Therefore, the first space 141 a acts as a part of the suction passage, the communication hole 150 a substantially acts as an exit of the suction passage, and the second space 141 b substantially acts as a suction chamber.
- the communication holes 150 a and the orifice 150 d are formed in the partition member 150 , these may be formed in the cylinder head 104 .
- the number of the communication holes 150 a is not limited to two, and it may be any number as long as it is one or more.
- a position of the communication hole 150 a is not limited to a position above the axis of the drive shaft 110 in a gravity direction, the communication hole 150 a may be positioned at any position as long as it is arranged above the orifice 150 d, and the position may be preferably adjusted depending on a target storage amount of lubricating oil in the first space 141 a.
- pressing protrusions 104 d protruding toward the valve plate 103 are formed on a surface of a suction chamber forming wall of the cylinder head 104 facing the valve plate 103 , i.e., on a bottom wall 104 c of the suction chamber 141 , and are arranged in a substantially annular manner.
- the pressing protrusions 104 d press, toward the valve plate 103 , a flat portion 139 b of the head gasket 139 formed between the guide passages 141 b 2 at a periphery of the partition member 150 , and accordingly press the valve plate 103 via the head gasket 139 and the discharge valve forming body 138 .
- the partition member 150 can be reliably retained on the valve plate 103 side.
- the pressing protrusions 104 d correspond to a protruded portion according to the present invention.
- the pressure introducing passage 147 includes: a communication hole 138 c formed in the discharge valve forming body 138 ; a long hole 103 d formed in the valve plate 103 ; a communication hole 138 d formed in the discharge valve forming body 138 ; a communication hole 139 d formed in the head gasket 139 ; a communication hole 104 e formed in the pressing protrusion 104 d formed in the cylinder head 104 as illustrated in FIG. 9 ; and a space 104 f partitioned by two O rings 313 a and 313 b in the receiving space of the control valve 300 in the cylinder head 104 , and connected to the communication hole 301 e of the control valve 300 , as illustrated in FIG. 9 .
- the long hole 103 d is closed by a suction valve forming body (not illustrated) arranged between the cylinder block 101 and the valve plate 103 .
- a pressure in the second space 141 b of the suction chamber 141 is introduced to the second pressure-sensitive chamber 307 of the control valve 300 via this pressure introducing passage 147 and the communication hole 301 e.
- An open end of the pressure introducing passage 147 on the second space 141 b side is the communication hole 138 c.
- the communication hole 138 c is arranged above, in a gravity direction, the orifice 150 d formed in the partition member 150 .
- variable-displacement compressor having such a configuration, according to the present embodiment, from an inflow refrigerant gas containing a lubricating oil, which has flowed into the first space 141 a from the suction passage 104 a, the lubricating oil is separated in the first space 141 a.
- the separated lubricating oil is stored in the bottom portion (lower side in a gravity direction) of the first space 141 a.
- control valve 300 especially the second pressure-sensitive chamber 307 and the inside of the cylindrical member 312 communicating with the second pressure-sensitive chamber 307 , are not filled with the lubricating oil, and sensitivity of the control valve 300 is not reduced by operation failure caused by inflow of the lubricating oil.
- the orifice 150 d formed in the partition member 150 when the lubricating oil stored in the first space 141 a is returned to the second space 141 b via the orifice 150 d, the lubricating oil does not flow into the pressure introducing passage 147 , and control operation of the control valve 300 is not interrupted.
- the lubricating oil gradually flowing into the second space 141 b from the first space 141 a by the orifice 150 d contributes to lubricate each component of the variable-displacement compressor 100 .
- the lubricating oil separated from the refrigerant gas is drawn into the cylinder bore 101 a, and therefore an oil flowing out from the variable-displacement compressor 100 toward an air conditioning system is reduced. Accordingly it contributes to reduce an oil circulation rate.
- each suction hole 103 a is partitioned by the guide passages 141 b 2 radially formed from the central space 141 b 1 , the refrigerant gas smoothly flows toward each suction hole 103 a, and thus, mutual interference of a refrigerant gas toward each suction hole 103 a is prevented. Accordingly it contributes to reduce a pulsation level of a suction pressure.
- the partition member 150 is integrally formed with the head gasket 139 by stamping the head gasket 139 , an additional new component as a partition member is not needed, and a structure for fixing the partition member 150 in the suction chamber 141 is not needed. As a result, a cost increase by employing the partition member 150 can be suppressed.
- the partition member 150 is integrally formed with the head gasket 139 .
- the partition member 150 may be formed to be a member separated from the head gasket 139 .
- the lubricating oil stored in the first space 141 a is returned to the second space 141 b by the orifice 150 d.
- the first space 141 a and the crank chamber 140 may be communicated by an oil return passage. In this manner, even when the variable-displacement compressor 100 stops rotating, oil stored in the first space 141 a can be returned to the crank chamber 140 .
- the communication hole 150 a is provided in the embodiment as a communication passage for introducing the refrigerant gas, from which the oil has been separated, to the second space 141 b, a cylindrical communication passage protruding to the first space 141 a may be provided instead of the hole. This may improve an oil separation effect in the first space 141 a.
- variable-displacement compressor 100 an electromagnetic clutch may be mounted on a variable-displacement compressor.
- the present invention is not limited to a swash plate type, and it is applicable to a swing-plate type variable-displacement compressor.
Abstract
To prevent operation failure caused by adhesion of a lubricating oil of a control valve for controlling a discharge displacement. A partition member 150 is provided to partition a suction chamber 141 into: a first space 141 a, to which a suction passage is connected, and in which a lubricating oil is separated from a refrigerant gas and is stored; and a second space 141 b, to which a suction hole 103 a is connected, and to which the refrigerant gas from which the lubricating oil that has been separated is introduced via a communication hole 150 a, and it is configured so that a pressure in the second space 141 b can be introduced to a control valve 300 via a pressure introducing passage 147.
Description
- The present invention relates to a variable-displacement compressor, and more specifically, relates to a variable-displacement compressor that varies a discharge displacement of a refrigerant gas by controlling a pressure in a crank chamber by a control valve depending on a pressure in a suction chamber.
- For example, Patent Document 1 discloses this type of a variable-displacement compressor. In the variable-displacement compressor, a control valve is provided in a communication passage communicating between a discharge chamber and a crank chamber on a back side of a piston. The control valve controls a pressure in the crank chamber by controlling an opening of the communication passage depending on a pressure in a suction chamber, and a stroke of the piston is changed. Accordingly, a discharge displacement of a refrigerant gas is varied. Specifically, the suction chamber is connected to the control valve by a pressure introducing passage, and a pressure in the suction chamber is introduced to the control valve. The control valve controls an opening of the communication passage by detecting a change in a pressure in the suction chamber, an amount of a high pressure refrigerant gas to be introduced to the crank chamber is increased or decreased, and a stroke of the piston is changed by changing an inclination (angle of inclination) of a swash plate. Accordingly, a discharge displacement of a refrigerant gas is increased or decreased.
- Patent Document 1: Japanese Patent Application Laid-open Publication No. 2012-127233
- In such a variable-displacement compressor, a lubricating oil is mixed in a refrigerant gas to lubricate each component of the compressor. Therefore, in a configuration like a conventional variable-displacement compressor, in which a refrigerant gas including a lubricating oil to be returned from a suction passage to a suction chamber via an external refrigerant circuit after being discharged from the compressor is directly introduced to a control valve from a pressure introducing passage, sensitivity of the control valve might be lowered since the lubricating oil flows into the control valve especially in a case in which a large amount of the oil is circulating.
- The present invention is focused on the above issue and seeks to provide a variable-displacement compressor that can control an amount of a lubricating oil flowing into a control valve and prevent sensitivity reduction of the control valve caused by inflow of the lubricating oil.
- Therefore, a variable-displacement compressor according to the present invention includes: a piston that compresses a refrigerant gas drawn from a suction chamber via a suction hole and discharges the refrigerant gas to a discharge chamber via a discharge hole; a first passage that communicates between a crank chamber on a back side of the piston and the discharge chamber; a control valve provided in the first passage and that controls an opening of the first passage; a second passage that communicates between the crank chamber and the suction chamber, and that is provided with an orifice; and a pressure introducing passage configured to introduce a pressure in the suction chamber to the control valve. The control valve controls an opening of the first passage depending on the pressure in the suction chamber, which has been introduced from the pressure introducing passage, so as to control a pressure in the crank chamber, so that a stroke of the piston is changed, and accordingly, a discharge displacement of a refrigerant gas is varied. The suction chamber includes a storage area for separating a lubricating oil from a refrigerant gas inflowing from a suction passage and for storing the lubricating oil, and the pressure introducing passage is open to an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows, so as to introduce the pressure in the suction chamber to the control valve.
- According to the variable-displacement compressor according to the present invention, the suction chamber includes the storage area for storing the lubricating oil separated from the refrigerant gas inflowed from the suction passage, and the pressure introducing passage is open to an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows. Therefore, an amount of the lubricating oil in the refrigerant gas flowing into the control valve via the pressure introducing passage can be reduced, and sensitivity reduction of the control valve caused by inflow of the lubricating oil can be prevented.
-
FIG. 1 is a cross-sectional view illustrating an embodiment of a variable-displacement compressor according to the present invention. -
FIG. 2 is a cross-sectional view of a control valve applied to the embodiment. -
FIG. 3 is a view illustrating a valve plate viewed from a cylinder block side, according to the embodiment. -
FIG. 4 is a view illustrating a discharge valve forming body viewed from a cylinder block side, according to the embodiment. -
FIG. 5 is a view illustrating a cylinder head viewed from a cylinder block side, according to the embodiment. -
FIG. 6 is a view illustrating a head gasket viewed from a cylinder block side, according to the embodiment. -
FIG. 7 is a cross-sectional view taken along with a line A-O-A viewed from arrows A, in a state in which the head gasket illustrated inFIG. 6 is assembled. -
FIG. 8 is a cross-sectional view taken along with a line viewed from arrows B, illustrated inFIG. 6 . -
FIG. 9 is a cross-sectional view taken along with a line viewed from arrows C, in a state in which the cylinder head illustrated inFIG. 5 is assembled. - Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
-
FIG. 1 illustrates a schematic configuration of a variable-displacement compressor according to a first embodiment of the present invention, andFIG. 1 is an example of a clutch-less variable-displacement compressor for use in a vehicle air conditioning system. - In
FIG. 1 , a variable-displacement compressor 100 includes: acylinder block 101 in whichmultiple cylinder bores 101 a are formed; afront housing 102 provided at one end of thecylinder block 101; and acylinder head 104 provided at another end of thecylinder block 101 via avalve plate 103. - A
drive shaft 110 is provided so as to cross in acrank chamber 140 formed by thecylinder block 101 and thefront housing 102. Aswash plate 111 is arranged around an intermediate portion in an axial direction of thedrive shaft 110. Theswash plate 111 is connected to arotor 112, which is fixed to thedrive shaft 110, via alinkage 120, and is supported so that an inclination thereof can be varied by thedrive shaft 110. - The
linkage 120 includes: afirst arm 112 a arranged so as to protrude from therotor 112; asecond arm 111 a arranged so as to protrude from theswash plate 111; and alink arm 121 rotatably connected at one end to thefirst arm 112 a via afirst connection pin 122, and rotatably connected at the other end to thesecond arm 111 a via thesecond connection pin 123. - A through
hole 111 b of theswash plate 111 is formed so as to be inclined within a range of the maximum inclination (θ max) to the minimum inclination (θ min). A minimum-inclination restricting portion coming into contact with thedrive shaft 110 is formed to the throughhole 111 b. In a case in which an inclination of theswash plate 111 orthogonal to thedrive shaft 110 is set as 0°, the minimum inclination restricting portion of the throughhole 111 b allows theswash plate 111 to be inclined to approximately 0°. The maximum inclination of theswash plate 111 is restricted when theswash plate 111 comes into contact with therotor 112. - A
disinclining spring 114 for biasing theswash plate 111 toward the minimum inclination is mounted around thedrive shaft 110 between therotor 112 and theswash plate 111. Also, an incliningspring 115 for biasing the swash plate 11 in a direction increasing an inclination of theswash plate 111 is mounted around thedrive shaft 110 between theswash plate 111 and aspring support member 116 provided to thedrive shaft 110. Herein, a biasing force of the incliningspring 115 at the minimum inclination is set to be greater than that of thedisinclining spring 114. When thedrive shaft 110 is not rotating, theswash plate 111 is arranged at an inclination angle at which the biasing force of thedisinclining spring 114 and the biasing force of the incliningspring 115 are balanced. - One end of the
drive shaft 110 is extended to an outer side of thefront housing 102, passing through aboss portion 102 a of thefront housing 102, and connected to a power transmission device (not illustrated). Ashaft seal device 130 is inserted between thedrive shaft 110 and theboss portion 102 a to block the inside of thecrank chamber 140 from the outside. - The connected body of the
drive shaft 110 and therotor 112 is supported bybearings bearing 133 and athrust plate 134 in a thrust direction. A gap between thethrust plate 134 of thedrive shaft 110 and a portion coming into contact with thethrust plate 134 is adjusted to a predetermined gap by an adjustingscrew 135. Power from an external driving source (vehicle engine) is transmitted to a power transmission device, and thedrive shaft 110 rotates in synchronization with the power transmission device. - A
piston 136 is arranged in thecylinder bore 101 a. An outer periphery of theswash plate 111 is accommodated in an internal space of an end portion of thepiston 136 protruding toward thecrank chamber 140. Theswash plate 111 is synchronized with thepiston 136 via a pair ofshoes 137. Therefore, thepiston 136 reciprocates in the cylinder bore 101 a by rotation of theswash plate 111. - In the
cylinder head 104, asuction chamber 141 defined by anannular partition wall 104 b is formed at a center thereof, and adischarge chamber 142 defined by thepartition wall 104 b and an external wall is formed so that thedischarge chamber 142 circularly surrounds thesuction chamber 141. Thesuction chamber 141 is communicated with thecylinder bore 101 a via asuction hole 103 a formed in thevalve plate 103 and a suction valve (not illustrated) formed in a suction valve forming body. Thedischarge chamber 142 is communicated with thecylinder bore 101 a via adischarge hole 103 b formed in thevalve plate 103 and adischarge valve 138 a formed in a dischargevalve forming body 138, illustrated inFIG. 4 . - A compressor housing is formed by fixing, with multiple through
bolts 105, thefront housing 102, a center gasket (not illustrated), thecylinder block 101, a cylinder gasket (not illustrated), the suction valve forming body (not illustrated), thevalve plate 103 illustrated inFIG. 3 , the dischargevalve forming body 138 illustrated inFIG. 4 , ahead gasket 139 illustrated inFIG. 6 , and thecylinder head 104 illustrated inFIG. 5 . - In the
cylinder head 104, asuction passage 104 a is formed to communicate between a low pressure side refrigerant circuit (suction side refrigerant circuit) of a vehicle air conditioning system (refrigerant device) and thesuction chamber 141. Accordingly, thesuction chamber 141 is connected to the low pressure side refrigerant circuit of the refrigerant device. Thesuction passage 104 a is linearly extended so as to cross a part of thedischarge chamber 142 toward thesuction chamber 141 from the outside of thecylinder head 104. - The
suction chamber 141 is partitioned into afirst space 141 a connected to thesuction passage 104 a and asecond space 141 b connected to thesuction hole 103 a by apartition member 150 integrally formed with thehead gasket 139. Thefirst space 141 a and thesecond space 141 b are communicated by acommunication hole 150 a (illustrated inFIG. 6 ) formed in thepartition member 150 as a communication passage. Thefirst space 141 a is configured to allow a low pressure refrigerant gas to flow into thefirst space 141 a from a low pressure side refrigerant circuit via thesuction passage 104 a, and thefirst space 141 a is configured to separate a lubricating oil mixed in the refrigerant gas and to store the separated lubricating oil at a lower side thereof in a gravity direction (bottom portion of the space). Therefore, thefirst space 141 a corresponds to a storage area according to the present invention. Thesecond space 141 b is configured to introduce a refrigerant gas, which has flowed into thesecond space 141 b through thecommunication hole 150 a from thefirst space 141 a and separated from a lubricating oil, to thesuction hole 103 a. Therefore, thesecond space 141 b corresponds to an inflow area according to the present invention. Thepartition member 150 will be described in detail below. - A
muffler 160 for reducing noise and vibration caused by refrigerant pulsation is provided on thecylinder block 101 at an upper portion thereof. Themuffler 160 is formed by fixing alid member 106 with a bolt via a sealing member (not illustrated) to a formingwall 101 b divisionally formed at the upper portion of thecylinder block 101. Acheck valve 200 is arranged in amuffler space 143 in themuffler 160, to reduce a backward flow of a refrigerant gas from a discharge side refrigerant circuit to thedischarge chamber 142. - The
check valve 200 is arranged at a connecting portion between acommunication passage 144 and themuffler space 143, thecommunication passage 144 extending across thecylinder head 104, thevalve plate 103, and thecylinder block 101 and communicating with thedischarge chamber 142. Thecheck valve 200 operates in response to a pressure difference between the communication passage 144 (upstream side) and the muffler space 143 (downstream side). When the pressure difference is less than a predetermined value, thecheck valve 200 blocks thecommunication passage 144. When the pressure difference is greater than the predetermined value, thecheck valve 200 opens thecommunication passage 144. Therefore, thedischarge chamber 142 is connected to a discharge side refrigerant circuit of a vehicle air conditioning system via a discharge passage including thecommunication passage 144, thecheck valve 200, themuffler space 143, and adischarge port 106 a. - In the
cylinder head 104, acontrol valve 300 is provided. - The
control valve 300 is provided in apressure supply passage 145 provided as a first passage that communicates between thedischarge chamber 142 and thecrank chamber 140 on a back side of thepiston 136. Thecontrol valve 300 adjusts an opening of thepressure supply passage 145 and controls an amount of the discharge refrigerant gas to be introduced to the crankchamber 140. Also, a refrigerant in thecrank chamber 140 flows to thesecond space 141 b of thesuction chamber 141 via apressure releasing passage 146 provided as a second passage that passes through thecommunication passage 101 c, aspace 101 d, anorifice 103 c formed in thevalve plate 103 illustrated inFIG. 3 , and acommunication hole 138 b formed in the dischargevalve forming body 138 illustrated inFIG. 4 . Thus, thecontrol valve 300 changes the pressure in thecrank chamber 140, which in turn changes the inclination of theswash plate 111, that is, a stroke of thepiston 136. As a result, a discharge displacement of the variable-displacement compressor 100 can be varied. Although theorifice 103 c is a fixed orifice in the embodiment, theorifice 103 c may be a variable orifice. - The
control valve 300 according to the embodiment is a control valve that operates in response to an external electrical signal.FIG. 2 illustrates a configuration thereof. - The control valve 300 includes: a first pressure-sensitive chamber 302 that is formed in a valve housing 301 and communicates with the crank chamber 140 by the pressure supply passage 145 on the crank chamber 140 side via a communication hole 301 a; a valve chamber 303 that communicates with the discharge chamber 142 by the pressure supply passage 145 on the discharge chamber 142 side via a communication hole 301 b; a valve hole 301 c that is open at one end thereof to the first pressure-sensitive chamber 302 and is open at the other end thereof to the valve chamber 303; a valve body 304, one end of which is arranged in the valve chamber 303 and opens and closes the valve hole 301 c, the valve body 304 being slidably supported by a support hole 301 d formed in the valve housing 301; a bellows assembly 305 that is provided with a spring in an evacuated inside thereof, and is arranged in the first pressure-sensitive chamber 302, the bellows assembly 305 receiving a pressure in the crank chamber 140; a connecting portion 306 that is attachably and detachably connected to the bellows assembly 305 at one end thereof and is fixed to one end of the valve body 304 at the other end thereof; a second pressure-sensitive chamber 307 that is blocked from the valve chamber 303, and in which the other end of the valve body 304 is arranged, the second pressure-sensitive chamber 307 communicating with the second space 141 b of the suction chamber 141 by a pressure introducing passage 147, to be described later, via a communication hole 301 e; a solenoid rod 304 a that is integrally formed with the valve body 304, and in which a movable core 308 is press-fitted at an end portion of the solenoid rod 304 a opposite to the valve body 304; a fixed core 309 that is arranged at an outer periphery of the solenoid rod 304 a and is arranged to face the movable core 308, being spaced with a predetermined gap; a spring 310 that is interposed between the fixed core 309 and the movable core 308, and elastically biases the valve body 304 in a valve opening direction via the movable core 308 and the solenoid rod 304 a; a cylindrical member 312 that is arranged at an outer periphery of the fixed core 309 and fixed to a solenoid housing 311, and that is made of a nonmagnetic material; and an electromagnetic coil 313 that is accommodated in the solenoid housing 311 so as to surround the cylindrical member 312. Also, three O rings 313 a to 313 c are arranged at an outer periphery of the
control valve 300. By the O rings 313 a to 313 c, a receiving space of thecontrol valve 300 formed in thecylinder head 104 is partitioned into an area in which a pressure in thecrank chamber 140 is applied, an area in which a pressure in thedischarge chamber 142 is applied, and an area in which a pressure in thesuction chamber 141 is applied. - In the
control valve 300 having such a configuration, if a bellows effective area Sb of thebellows assembly 305, a pressure receiving area Sv for receiving a pressure in thecrank chamber 140 applied to thevalve body 304 from thevalve hole 301 c side, a pressure receiving area Sr for receiving a pressure in the suction chamber 141 (second space 141 b) applied to thevalve body 304 in the second pressure-sensitive chamber 307 are set to approximately the same value, a force acting on thevalve body 304 is represented by the following formula (1): -
Ps=−(1/Sb)·F(i)+(F+f)/Sb (1) - where, Ps denotes a pressure in the suction chamber 141 (
second space 141 b), F(i) denotes an electromagnetic force, f denotes a biasing force of thespring 310, and F denotes a biasing force of thebellows assembly 305. - Therefore, the
control valve 300 adjusts an opening of thepressure supply passage 145 communicating between thedischarge chamber 142 and thecrank chamber 140 so that a pressure Ps in the suction chamber 141 (second space 141 b), which has been introduced via thepressure introducing passage 147, is maintained to a predetermined value determined based on a current flowing to anelectromagnetic coil 313 in response to an external signal, to thereby control an amount of a discharge refrigerant gas to be introduced to the crankchamber 140, to control a discharge displacement of the variable-displacement compressor 100. The pressure Ps in the suction chamber 141 (second space 141 b) can be varied from the outside by adjusting a current flowing to theelectromagnetic coil 313. - While an air conditioner is operating, i.e., in a state in which the variable-
displacement compressor 100 is operating, an energization amount of theelectromagnetic coil 313 is adjusted based on an external signal, a discharge displacement is variably controlled so that a pressure in the suction chamber 141 (second space 141 b) becomes a predetermined value and a pressure in thesuction chamber 141 is appropriately controlled in response to the external environment. Although thecontrol valve 300 in the embodiment operates in response to an external signal, a mechanical control valve that operates by sensing a pressure in a suction chamber may be used. - Next, the above-described
partition member 150 and thepressure introducing passage 147 will be described in detail with reference toFIGS. 3 to 9 . - The
partition member 150 is integrally formed by making a center of thehead gasket 139 illustrated inFIG. 6 , i.e., a portion facing thesuction chamber 141 at a center of thecylinder head 104, protrude toward thesuction chamber 141 by stamping. By thepartition member 150, thesuction chamber 141 is partitioned into thefirst space 141 a to which thesuction passage 104 a is connected, and thesecond space 141 b to which thesuction hole 103 a is connected. In thehead gasket 139, aretainer 139 a for restricting an opening of thedischarge valve 138 a is formed in an area corresponding to thedischarge chamber 142. Thehead gasket 139 is a rubber-coated metal thin plate. Therefore, thepartition member 150 integrally formed with thehead gasket 139 is also rubber-coated. - The
second space 141 b partitioned by thepartition member 150 includes, as illustrated inFIG. 7 , acentral space 141 b 1 and guidepassages 141 b 2 radially extended toward the suction holes 103 a from thecentral space 141 b 1. Theguide passage 141 b 2 includes abottom wall 150 b andside walls 150 c as illustrated inFIG. 8 . As illustrated inFIG. 7 , theguide passage 141 b 2 includes an area in which thebottom wall 150 b is inclined so that a passage sectional area is reduced toward each of the suction holes 103 a, which are formed in thevalve plate 103 to be annularly arranged at approximately equal intervals around an axis O of thedrive shaft 110 at an approximately equal distance from the axis O of thedrive shaft 110. - Furthermore, in the
partition member 150, twocommunication holes 150 a that communicate between thefirst space 141 a and thesecond space 141 b are formed to be open to twoguide passages 141 b 2 as illustrated inFIG. 6 . Thecommunication hole 150 a is formed by adjusting the position thereof so that a predetermined amount of a lubricating oil can be stored in thefirst space 141 a. Specifically, thecommunication hole 150 a is open to a position that is above the axis O of thedrive shaft 110 in a gravity direction and outside an area on an extension of thesuction passage 104 a into thesuction chamber 141, in order to prevent a main flow of a suction refrigerant, which has flowed into thefirst space 141 a from thesuction passage 104 a, from directly flowing into thecommunication hole 150 a. Also, anorifice 150 d that communicates between thefirst space 141 a and thesecond space 141 b is formed in thebottom wall 150 b of theguide passage 141 b 2 positioned below the axis O of thedrive shaft 110 in a gravity direction. An upper side inFIGS. 3 to 6 is an upper side in a gravity direction. - Since the
communication hole 150 a is located above the axis O of thedrive shaft 110 in a gravity direction, thefirst space 141 a acts as an oil storage chamber for storing a lubricating oil returned from an air conditioning system with an inflow refrigerant gas. An opening area of theorifice 150 d is set so that an appropriate amount of a lubricating oil is stored in thefirst space 141 a. Theorifice 150 d acts as an oil return passage, which gradually returns a lubricating oil stored in thefirst space 141 a to thesecond space 141 b. Therefore, thefirst space 141 a acts as a part of the suction passage, thecommunication hole 150 a substantially acts as an exit of the suction passage, and thesecond space 141 b substantially acts as a suction chamber. - Although the communication holes 150 a and the
orifice 150 d (oil return passage) are formed in thepartition member 150, these may be formed in thecylinder head 104. Also, the number of the communication holes 150 a is not limited to two, and it may be any number as long as it is one or more. Furthermore, although a position of thecommunication hole 150 a is not limited to a position above the axis of thedrive shaft 110 in a gravity direction, thecommunication hole 150 a may be positioned at any position as long as it is arranged above theorifice 150 d, and the position may be preferably adjusted depending on a target storage amount of lubricating oil in thefirst space 141 a. - Multiple
pressing protrusions 104 d protruding toward thevalve plate 103 are formed on a surface of a suction chamber forming wall of thecylinder head 104 facing thevalve plate 103, i.e., on abottom wall 104 c of thesuction chamber 141, and are arranged in a substantially annular manner. Thepressing protrusions 104 d press, toward thevalve plate 103, aflat portion 139 b of thehead gasket 139 formed between theguide passages 141 b 2 at a periphery of thepartition member 150, and accordingly press thevalve plate 103 via thehead gasket 139 and the dischargevalve forming body 138. In this manner, thepartition member 150 can be reliably retained on thevalve plate 103 side. Herein, thepressing protrusions 104 d correspond to a protruded portion according to the present invention. - The
pressure introducing passage 147 includes: acommunication hole 138 c formed in the dischargevalve forming body 138; along hole 103 d formed in thevalve plate 103; acommunication hole 138 d formed in the dischargevalve forming body 138; acommunication hole 139 d formed in thehead gasket 139; acommunication hole 104 e formed in thepressing protrusion 104 d formed in thecylinder head 104 as illustrated inFIG. 9 ; and aspace 104 f partitioned by two O rings 313 a and 313 b in the receiving space of thecontrol valve 300 in thecylinder head 104, and connected to thecommunication hole 301 e of thecontrol valve 300, as illustrated inFIG. 9 . Thelong hole 103 d is closed by a suction valve forming body (not illustrated) arranged between thecylinder block 101 and thevalve plate 103. - Therefore, a pressure in the
second space 141 b of thesuction chamber 141 is introduced to the second pressure-sensitive chamber 307 of thecontrol valve 300 via thispressure introducing passage 147 and thecommunication hole 301 e. An open end of thepressure introducing passage 147 on thesecond space 141 b side is thecommunication hole 138 c. Thecommunication hole 138 c is arranged above, in a gravity direction, theorifice 150 d formed in thepartition member 150. - In the variable-displacement compressor having such a configuration, according to the present embodiment, from an inflow refrigerant gas containing a lubricating oil, which has flowed into the
first space 141 a from thesuction passage 104 a, the lubricating oil is separated in thefirst space 141 a. The separated lubricating oil is stored in the bottom portion (lower side in a gravity direction) of thefirst space 141 a. The remaining refrigerant gas, from which the lubricating oil has been separated, flows into thesecond space 141 b via thecommunication hole 150 a, and flows toward eachsuction hole 103 a along theguide passages 141 b 2, and then is drawn into the cylinder bore 101 a from eachsuction hole 103 a by the reciprocation of thepiston 136. - In this manner, since what flows into the
second space 141 b of thesuction chamber 141 is the remaining refrigerant gas, from which the lubricating oil has been separated, an amount of the lubricating oil flowing into the second pressure-sensitive chamber 307 of thecontrol valve 300, to which a pressure in thesecond space 141 b is introduced via thepressure introducing passage 147, can be reduced. - Therefore, the inside of the
control valve 300, especially the second pressure-sensitive chamber 307 and the inside of thecylindrical member 312 communicating with the second pressure-sensitive chamber 307, are not filled with the lubricating oil, and sensitivity of thecontrol valve 300 is not reduced by operation failure caused by inflow of the lubricating oil. - Also, since the
communication hole 138 c, which is an open end of thepressure introducing passage 147 on thesecond space 141 b side, is arranged above, in a gravity direction, theorifice 150 d formed in thepartition member 150, when the lubricating oil stored in thefirst space 141 a is returned to thesecond space 141 b via theorifice 150 d, the lubricating oil does not flow into thepressure introducing passage 147, and control operation of thecontrol valve 300 is not interrupted. The lubricating oil gradually flowing into thesecond space 141 b from thefirst space 141 a by theorifice 150 d contributes to lubricate each component of the variable-displacement compressor 100. - The lubricating oil separated from the refrigerant gas is drawn into the cylinder bore 101 a, and therefore an oil flowing out from the variable-
displacement compressor 100 toward an air conditioning system is reduced. Accordingly it contributes to reduce an oil circulation rate. - Furthermore, since each
suction hole 103 a is partitioned by theguide passages 141 b 2 radially formed from thecentral space 141 b 1, the refrigerant gas smoothly flows toward eachsuction hole 103 a, and thus, mutual interference of a refrigerant gas toward eachsuction hole 103 a is prevented. Accordingly it contributes to reduce a pulsation level of a suction pressure. - In the present embodiment, since the
partition member 150 is integrally formed with thehead gasket 139 by stamping thehead gasket 139, an additional new component as a partition member is not needed, and a structure for fixing thepartition member 150 in thesuction chamber 141 is not needed. As a result, a cost increase by employing thepartition member 150 can be suppressed. - In the present embodiment, the
partition member 150 is integrally formed with thehead gasket 139. However, thepartition member 150 may be formed to be a member separated from thehead gasket 139. - Furthermore, in the present embodiment, the lubricating oil stored in the
first space 141 a is returned to thesecond space 141 b by theorifice 150 d. However, thefirst space 141 a and thecrank chamber 140 may be communicated by an oil return passage. In this manner, even when the variable-displacement compressor 100 stops rotating, oil stored in thefirst space 141 a can be returned to the crankchamber 140. - Although the
communication hole 150 a is provided in the embodiment as a communication passage for introducing the refrigerant gas, from which the oil has been separated, to thesecond space 141 b, a cylindrical communication passage protruding to thefirst space 141 a may be provided instead of the hole. This may improve an oil separation effect in thefirst space 141 a. - Although an example of a clutch-less compressor as the variable-
displacement compressor 100 is illustrated in the embodiment, an electromagnetic clutch may be mounted on a variable-displacement compressor. The present invention is not limited to a swash plate type, and it is applicable to a swing-plate type variable-displacement compressor. - 100 Variable-displacement compressor
- 103 a Suction hole
- 103 c Orifice
- 104 a Suction passage
- 136 Piston
- 140 Crank chamber
- 141 Suction chamber
- 141 a First space
- 141 b Second space
- 142 Discharge chamber
- 145 Pressure supply passage (first passage)
- 146 Pressure releasing passage (second passage)
- 147 Pressure introducing passage
- 150 Partition member
- 150 a Communication hole
- 300 Control valve
Claims (5)
1. A variable-displacement compressor comprising:
a piston that compresses a refrigerant gas drawn from a suction chamber via a suction hole and discharges the refrigerant gas to a discharge chamber via a discharge hole;
a first passage that communicates between a crank chamber on a back side of the piston and the discharge chamber;
a control valve provided in the first passage and that controls an opening of the first passage;
a second passage that communicates between the crank chamber and the suction chamber, and that is provided with an orifice; and
a pressure introducing passage configured to introduce a pressure in the suction chamber to the control valve,
wherein the control valve controls an opening of the first passage depending on the pressure in the suction chamber, which has been introduced from the pressure introducing passage, so as to control a pressure in the crank chamber, so that a stroke of the piston is changed, and accordingly, a discharge displacement of a refrigerant gas is varied,
wherein the suction chamber includes a storage area for separating a lubricating oil from a refrigerant gas inflowing from a suction passage and for storing the lubricating oil, and an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows,
wherein the second passage is open to the inflow area, and
wherein the pressure introducing passage is open to an inflow area into which the refrigerant gas, from which the lubricating oil has been separated, flows, so as to introduce the pressure in the suction chamber to the control valve.
2. The variable-displacement compressor according to claim 1 , wherein the suction chamber is partitioned, by a partition member, into a first space to which the suction passage is open, and that acts as the storage area, and a second space to which the suction hole and the pressure introducing passage are open, and that acts as the inflow area, wherein a communication passage that communicates between the first space and the second space is provided.
3. The variable-displacement compressor according to claim 2 , wherein the communication passage is formed in the partition member by adjusting a position thereof, so as to be capable of storing a predetermined amount of the lubricating oil in the first space.
4. The variable-displacement compressor according to claim 2 , wherein the partition member is formed by protruding, into a suction chamber, a portion of a head gasket facing a suction chamber, the head gasket being interposed between a valve plate, in which the suction hole and the discharge hole are formed, and a cylinder head, in which the suction chamber and the discharge chamber are formed.
5. The variable-displacement compressor according to claim 4 , wherein, on a surface of a suction chamber forming wall of the cylinder head facing the valve plate, a protruded portion for pressing a periphery of the partition member of the head gasket onto the valve plate, is formed to protrude.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012-246325 | 2012-11-08 | ||
JP2012246325A JP6005483B2 (en) | 2012-11-08 | 2012-11-08 | Variable capacity compressor |
PCT/JP2013/080329 WO2014073667A1 (en) | 2012-11-08 | 2013-11-08 | Variable-capacity compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150252797A1 true US20150252797A1 (en) | 2015-09-10 |
Family
ID=50684758
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/441,451 Abandoned US20150252797A1 (en) | 2012-11-08 | 2013-11-08 | Variable-Capacity Compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20150252797A1 (en) |
JP (1) | JP6005483B2 (en) |
DE (1) | DE112013005329T5 (en) |
WO (1) | WO2014073667A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190360476A1 (en) * | 2017-02-17 | 2019-11-28 | Hanon Systems | Swash plate type compressor |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR102590949B1 (en) | 2018-06-27 | 2023-10-19 | 한온시스템 주식회사 | Suction Damping Case |
JP7344792B2 (en) * | 2019-12-26 | 2023-09-14 | ダイハツ工業株式会社 | Oil passage structure |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4392788A (en) * | 1980-08-15 | 1983-07-12 | Diesel Kiki Co., Ltd. | Swash-plate type compressor having oil separating function |
US20120251343A1 (en) * | 2009-12-04 | 2012-10-04 | Sanden Corporation | Control Valve and Variable Capacity Swash-Plate Type Compressor Provided with same |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5738677A (en) * | 1980-08-15 | 1982-03-03 | Diesel Kiki Co Ltd | Compressor with swash plate |
JPH04276192A (en) * | 1991-03-05 | 1992-10-01 | Matsushita Electric Ind Co Ltd | Compressor |
JP2568714Y2 (en) * | 1992-06-01 | 1998-04-15 | 株式会社豊田自動織機製作所 | Piston type compressor |
JP4399994B2 (en) * | 2000-11-17 | 2010-01-20 | 株式会社豊田自動織機 | Variable capacity compressor |
JP2006077737A (en) * | 2004-09-13 | 2006-03-23 | Valeo Thermal Systems Japan Corp | Compressor |
JP5697022B2 (en) * | 2010-12-14 | 2015-04-08 | サンデン株式会社 | Variable capacity compressor |
-
2012
- 2012-11-08 JP JP2012246325A patent/JP6005483B2/en not_active Expired - Fee Related
-
2013
- 2013-11-08 US US14/441,451 patent/US20150252797A1/en not_active Abandoned
- 2013-11-08 DE DE112013005329.2T patent/DE112013005329T5/en not_active Withdrawn
- 2013-11-08 WO PCT/JP2013/080329 patent/WO2014073667A1/en active Application Filing
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4392788A (en) * | 1980-08-15 | 1983-07-12 | Diesel Kiki Co., Ltd. | Swash-plate type compressor having oil separating function |
US20120251343A1 (en) * | 2009-12-04 | 2012-10-04 | Sanden Corporation | Control Valve and Variable Capacity Swash-Plate Type Compressor Provided with same |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190360476A1 (en) * | 2017-02-17 | 2019-11-28 | Hanon Systems | Swash plate type compressor |
EP3584439A4 (en) * | 2017-02-17 | 2020-11-18 | Hanon Systems | Swash plate type compressor |
US11187219B2 (en) * | 2017-02-17 | 2021-11-30 | Hanon Systems | Swash plate type compressor |
Also Published As
Publication number | Publication date |
---|---|
JP2014095319A (en) | 2014-05-22 |
WO2014073667A1 (en) | 2014-05-15 |
JP6005483B2 (en) | 2016-10-12 |
DE112013005329T5 (en) | 2015-09-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10519944B2 (en) | Variable displacement compressor | |
US10670012B2 (en) | Variable displacement compressor for vehicle air conditioning system | |
US20050265853A1 (en) | Control valve for variable displacement compressor | |
US20150252797A1 (en) | Variable-Capacity Compressor | |
US11635152B2 (en) | Capacity control valve | |
US20170211561A1 (en) | Variable displacement swash plate type compressor | |
US20160320114A1 (en) | Flow rate measuring device and variable displacement compressor | |
WO2019139132A1 (en) | Variable capacity compressor | |
JP6469994B2 (en) | Compressor | |
US20150300711A1 (en) | Compressor | |
WO2020189604A1 (en) | Variable capacity compressor | |
JP6540954B2 (en) | Compressor | |
US9810209B2 (en) | Compressor | |
CN112334653B (en) | Variable displacement compressor | |
JP7213700B2 (en) | compressor | |
CN113272555B (en) | Compressor | |
WO2013065632A1 (en) | Compressor | |
WO2020026699A1 (en) | Variable capacity compressor | |
JP2021017884A (en) | Capacity control valve | |
JP2013002353A (en) | Compressor | |
JP2009287421A (en) | Variable displacement swash plate compressor | |
WO2014073668A1 (en) | Compressor | |
JP2018178791A (en) | Variable displacement compressor | |
JP2016169697A (en) | Variable capacity type swash plate compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SANDEN HOLDINGS CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TAGUCHI, YUKIHIKO;REEL/FRAME:035614/0124 Effective date: 20150423 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |