WO2014073620A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
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- WO2014073620A1 WO2014073620A1 PCT/JP2013/080161 JP2013080161W WO2014073620A1 WO 2014073620 A1 WO2014073620 A1 WO 2014073620A1 JP 2013080161 W JP2013080161 W JP 2013080161W WO 2014073620 A1 WO2014073620 A1 WO 2014073620A1
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- suction
- compressor
- space portion
- chamber
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
Definitions
- the present invention relates to a compressor that compresses refrigerant gas containing lubricating oil, and more particularly, to a technique for reducing the amount of lubricating oil flowing out from the compressor to an external refrigerant circuit.
- lubricating oil is mixed into refrigerant gas to lubricate the parts of the compressor in the crank chamber.
- the system efficiency is lowered. Therefore, the amount of lubricating oil flowing out from the compressor to the external refrigerant circuit is reduced, that is, the OCR (oil circulation rate) is reduced. Reduction is required.
- a centrifugal oil separator is provided in the discharge passage from the discharge chamber to separate the lubricating oil, thereby suppressing the outflow of the lubricating oil from the discharge passage. OCR is reduced.
- a centrifugal oil separator is provided in a passage communicating the crank chamber and the suction chamber to separate the lubricating oil and return it to the crank chamber. OCR is reduced by suppressing the outflow of lubricating oil.
- a compressor according to the present invention is a compressor that reciprocates a piston and compresses and discharges refrigerant gas sucked from a suction chamber through a suction hole.
- a partition member that divides the inflow suction chamber into a first space portion connected to the suction passage and a second space portion connected to the suction hole, the first space portion, and the second space portion.
- a communication passage for introducing the refrigerant gas from which the lubricating oil is separated from the first space portion to the second space portion.
- the suction chamber is partitioned into the first space portion and the second space portion by the partition member, the suction passage is connected to the first space portion, and the suction hole is connected to the second space portion. Then, since the refrigerant gas from which the lubricating oil is separated is introduced from the first space portion to the second space portion that is directly connected to the suction hole, the refrigerant gas from which the lubricating oil has been separated is compressed and discharged. be able to.
- the lubricating oil can be separated using the first space portion that is a part of the suction chamber, the outflow of the lubricating oil to the external refrigerant circuit is suppressed with a simple structure, and the OCR Can be reduced.
- the lubricating oil that has flowed out of the crank chamber is separated and stored in the first space portion, excessive lubricating oil is not stored in the crank chamber, and a decrease in oil viscosity during high-speed rotation can be suppressed. As a result, it is possible to reduce a risk that foreign matter stays in the crank chamber and abnormally wears the sliding portion inside the compressor.
- FIG. 6 is a partial cross-sectional view taken along the line AOA of FIG.
- FIG. 6 is a partial cross-sectional view taken along line BB in FIG. 5.
- FIG. 5 is a partial cross-sectional view taken along the line CC of FIG. 4.
- FIG. 1 is a sectional view of a swash plate type variable displacement compressor 100 as an example of a compressor to which the present invention is applied.
- the variable capacity compressor 100 is connected to a refrigerant circuit (evaporator and condenser) (not shown), reciprocates a piston 136, and compresses and discharges refrigerant gas sucked from the refrigerant circuit.
- the variable capacity compressor 100 is used in a vehicle air conditioner system.
- variable displacement compressor 100 includes a cylinder block 101 in which a plurality of cylinder bores 101 a of a piston 136 are formed, a front housing 102 provided at one end of the cylinder block 101, and the other end of the cylinder block 101. And a cylinder head 104 provided via a valve plate 103 and the like.
- crank block 140 behind the piston 136 is formed by the cylinder block 101 and the front housing 102, and a drive shaft 110 is provided so as to traverse the crank chamber 140 and is rotatably supported.
- a swash plate 111 is disposed around an intermediate portion in the axial direction of the drive shaft 110.
- a through hole 111b is formed at the center of the swash plate 111, and the drive shaft 110 is inserted through the through hole 111b.
- the swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 and rotating integrally with the drive shaft 110 via a link mechanism 120.
- the link mechanism 120 By this link mechanism 120, the swash plate 111 rotates together with the drive shaft 110 and the rotor 112, and its inclination angle with respect to the axis of the drive shaft 110 can be changed.
- the link mechanism 120 includes a first arm 112 a projecting from the rotor 112, a second arm 111 a projecting from the swash plate 111, and one end pivotable to the first arm 112 a via the first connecting pin 122. And a link arm 121 having the other end rotatably connected to the second arm 111a via a second connection pin 123.
- the through hole 111b of the swash plate 111 is formed in a shape that allows the swash plate 111 to tilt within a range from the maximum inclination angle to the minimum inclination angle.
- the through hole 111b is formed with a minimum inclination angle restricting portion that restricts the inclination angle displacement (tilting) of the swash plate 111 in the direction of reducing the inclination angle by coming into contact with the drive shaft 110. .
- the minimum inclination angle restricting portion is configured so that the inclination angle of the swash plate 111 is almost equal. It is formed so as to allow tilt angle displacement (tilt) up to 0 degree. Further, the tilt angle displacement (tilt) of the swash plate 111 in the direction of increasing the tilt angle is regulated by the swash plate 111 coming into contact with the rotor 112. Therefore, the inclination angle of the swash plate 111 becomes the maximum inclination angle when the swash plate 111 contacts the rotor 112.
- the drive shaft 110 includes an inclination angle reducing spring 114 that urges the swash plate 111 in a direction that decreases the inclination angle, and an inclination angle increasing spring 115 that urges the swash plate 111 in a direction that increases the inclination angle. It is mounted across the plate 111. Specifically, the inclination angle decreasing spring 114 is mounted between the swash plate 111 and the rotor 112, and the inclination angle increasing spring 115 is connected to the spring support member 116 provided on the swash plate 111 and the drive shaft 110. It is installed between.
- the urging force of the inclination angle increasing spring 115 is set to be larger than the urging force of the inclination angle decreasing spring 114. For this reason, when the drive shaft 110 is not rotating, that is, when the variable displacement compressor 100 is stopped, the swash plate 111 is biased by the inclination angle decreasing spring 114 and the urging force of the inclination angle increasing spring 115. Are located at an inclination angle (> minimum inclination angle) in which they are balanced.
- One end of the drive shaft 110 extends through the boss portion 102a of the front housing 102 to the outside of the front housing 102, and is connected to a power transmission device (not shown).
- a shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a, and the inside of the crank chamber 140 is blocked from the external space.
- the drive shaft 110 is supported by radial bearings 131 and 132 in the radial direction, and supported by a thrust plate 134 in the thrust direction.
- the thrust plate 134 side end of the drive shaft 110 and the thrust plate 134 are adjusted to have a predetermined gap by an adjustment screw 135.
- the drive shaft 110 rotates in synchronization with the power transmission device when power from an external drive source (not shown) is transmitted to the power transmission device.
- the rotor 112 is supported by the drive shaft 110 in the radial direction and supported by the thrust bearing 133 in the thrust direction.
- a piston 136 is disposed in the cylinder bore 101a, and an outer peripheral portion of the swash plate 111 is accommodated in an inner space of an end portion of the piston 136 that protrudes toward the crank chamber 140.
- the swash plate 111 includes a pair of shoes. It is linked with the piston 136 via 137. The shoe 137 converts the rotational movement of the swash plate 111 into the reciprocating movement of the piston 136, and the piston 136 reciprocates in the cylinder bore 101a.
- the cylinder head 104 is partitioned into a suction chamber 141 disposed on the extension of the axis O of the drive shaft 110 and a discharge chamber 142 disposed so as to surround the suction chamber 141 in an annular shape.
- the suction chamber 141 is connected to each cylinder bore 101a via a suction hole 103a formed in the valve plate 103 interposed between the valve plate 103 and the cylinder head 101, and a suction valve (not shown) formed in the suction valve forming body. Communicate with.
- Each discharge chamber 142 communicates with a corresponding cylinder bore 101a via a discharge valve 138a formed in the discharge valve forming body 138 and a discharge hole 103b formed in the valve plate 103.
- the suction chamber 141 and the discharge chamber 142 are partitioned by a partition wall 104b (see FIGS. 4, 6, and 8 described later).
- the partition wall 104b is formed in a substantially annular shape around the axis O of the drive shaft 110, and the entire suction chamber 141 has a substantially circular shape.
- the valve plate 103, the discharge valve forming body 138, the head gasket 139 and the cylinder head 104 are fastened by a plurality of through bolts 105 to form a housing.
- 2 shows the valve plate 103
- FIG. 3 shows the discharge valve forming body 138
- FIG. 4 shows the cylinder head 104
- FIG. 5 shows the head gasket 139.
- a suction passage 104a having a connection port 104a ' is formed, and this connection port 104a' is connected to the suction side refrigerant circuit (evaporator) of the above-described vehicle air conditioner system.
- the refrigerant gas flows into the suction chamber 141 from the suction passage 104a.
- the suction passage 104 a extends linearly from the outer periphery of the cylinder head 104 to the suction chamber 14 side so as to cross a part of the discharge chamber 142.
- the suction chamber 141 is partitioned by a partition member 150 into a first space portion 141a connected to the suction passage 104a and a second space portion 141b connected to the suction hole 103a.
- the partition member 150 communicates the first space portion 141a and the second space portion 141b, and introduces the refrigerant gas from which the lubricating oil is separated from the first space portion 141a to the second space portion 141b.
- a communication hole 150a is formed as a communication path. The partition member 150 and the communication hole 150a will be described in detail later.
- a muffler 143 is provided outside the cylinder block 101.
- the muffler 143 is formed by connecting a bottomed cylindrical lid member 106 to a cylindrical wall 101b erected on the outer surface of the cylinder block 101 via a seal member (not shown).
- a discharge port 106a is formed in the lid member 106, and the discharge port 106a is connected to a discharge side refrigerant circuit (condenser) of the vehicle air conditioner system.
- a communication path 144 that connects the muffler space 143a in the muffler 143 and the discharge chamber 142 is formed across the cylinder block 101, the valve plate 103, and the cylinder head 104.
- the muffler 143 and the communication path 144 are connected to the discharge chamber 142 and the discharge port.
- a discharge passage communicating with 106a is formed, and the muffler 143 forms a muffler space 143a along the discharge passage.
- a check valve 200 for opening and closing the inlet of the muffler 143 is disposed in the muffler 143.
- the check valve 200 is disposed at a connection portion between the communication path 144 and the muffler space 143a, and operates in response to a pressure difference between the communication path 144 (upstream side) and the muffler space 143 (downstream side).
- the valve is opened when the difference (pressure difference) between the pressure in the passage 144 (upstream pressure) Pu and the pressure in the muffler space 143 (downstream pressure) Pd is greater than a predetermined value SL (Pu ⁇ Pd> SL> 0).
- the valve is closed when the pressure difference is equal to or smaller than a predetermined value SL.
- the cylinder head 104 is further provided with a control valve 300.
- the control valve 300 adjusts the opening of the pressure supply passage 145 that connects the discharge chamber 142 and the crank chamber 140 to control the amount of discharge gas introduced into the crank chamber 140.
- the refrigerant gas in the crank chamber 140 flows to the suction chamber 141 (first space portion 141a) via the pressure release passage 146 (described in detail later).
- control valve 300 adjusts the amount of refrigerant introduced into the crank chamber 140 to change the pressure in the crank chamber 140 and changes the inclination angle of the swash plate 111, that is, the stroke of the piston 136, thereby compressing the variable capacity.
- the discharge capacity of the machine 100 can be variably controlled.
- control valve 300 adjusts the energization amount to a built-in solenoid based on an external signal, and is introduced into the pressure sensing chamber of the control valve 300 via a pressure introduction passage 147 (described in detail later).
- the discharge capacity is variably controlled so that the pressure in the suction chamber 141 (second space portion 141b) becomes a predetermined value, and the communication path 145 is forcibly opened by shutting off the energization to the solenoid, thereby changing the variable capacity.
- the discharge capacity of the compressor 100 is controlled to the minimum.
- the partition member 150 partitions the suction chamber 141 into the first space portion 141a connected to the suction passage 104a and the second space portion 141b connected to the suction hole 103a.
- the suction chamber 141 is partitioned into a second space portion 141b that is directly connected to the suction hole 103a and a first space portion 141a that is a space upstream of the second space portion.
- the partition member 150 is formed by projecting a head gasket 139 as will be described later.
- the second space portion 141 b has a central space 141 b 1 and each suction hole from the central space 141 b 1.
- the guide passage 141b2 that extends radially toward 103a and guides the intake refrigerant gas.
- the guide passage 141b2 is formed by a bottom wall 150b and a side wall 150c.
- the bottom wall 150b is inclined so that the cross-sectional area of the passage becomes smaller toward the suction hole 103a.
- a wall portion is formed.
- the communication hole 150a formed in the partition member 150 is located above the first space 141a in the direction of gravity, for example, above the axis O of the drive shaft 110 (the upper side in FIGS. 1 to 5 is the upper side in the direction of gravity).
- the first space portion 141a and the second space portion 141b are formed to communicate with each other at the position.
- the communication hole 150a opens at a position outside the region where the suction passage 104a extends into the suction chamber 141, and the main flow of the refrigerant gas flowing into the first space portion 141a from the suction passage 104a is on the downstream side. 2 It does not flow directly into the space 141b.
- the second space portion 141b since the second space portion 141b is directly connected to the suction hole 103a and is partitioned from the suction passage by the partition member 150, the second space portion 141b becomes a substantial suction chamber and is directly connected to the suction passage.
- the first space portion 141a that is formed can be regarded as a part of the suction passage, and the communication hole 150a is a substantial outlet of the suction passage.
- the communication hole 150a by forming the communication hole 150a so that the first space 141a and the second space 141b communicate with each other above the axis O of the drive shaft 110 in the gravitational direction, the first space 141a can be connected to the intake refrigerant gas.
- the oil storage chamber stores lubricating oil returned from the vehicle air conditioner system. In this way, the communication hole 150a communicates the first space 141a and the second space 141b, and introduces the refrigerant gas from which the lubricating oil is separated from the first space 141a to the second space
- a plurality of protrusions 104d are provided on the suction chamber forming wall surface of the cylinder head 104 facing the valve plate 103 to press the peripheral edge of the partition member portion of the head gasket 139 toward the valve plate.
- the protrusion 104d extends from the bottom wall 104c (the suction chamber forming wall surface) of the cylinder head 104 so as to press the region between the guide passages 141b2, and the head gasket 139 and the discharge valve forming body.
- the valve plate 103 is pressed via 138 and is arranged in an annular shape around the center of the cylinder head 104 at substantially equal intervals (see FIG. 4).
- the suction holes 103a (see FIG. 2 and the like) formed in the valve plate 103 have the same distance from the axis O of the drive shaft 110, and are arranged annularly around the axis of the drive shaft 110 at substantially equal intervals. .
- the partition member 150 is formed, for example, by projecting a portion of the head gasket 139 facing the suction chamber 141 into the suction chamber. Specifically, an area corresponding to the suction chamber 141 of the head gasket 139 is projected, and the partition member 150 is formed using the head gasket 139. For this reason, it is not necessary to add a new part as the partition member 150, and it is not necessary to additionally add a structure for fixing the partition member 150 in the suction chamber 141. Therefore, an increase in cost due to the provision of the partition member 150 can be suppressed.
- the head gasket 139 is a metal thin plate that is rubber-coated, and the partition member 150 is integrally pressed with the head gasket 139 to be subjected to rubber coating.
- the head gasket 139 is formed with a retainer 139a for regulating the opening of the discharge valve 138a in a region corresponding to the discharge chamber 142 on the radially outer side.
- Both sides of the side wall 150c in the portion where the guide passage 141b2 of the partition member 150 is formed are flat portions 139b of the head gasket 139.
- the partition member 150 is moved to the valve plate 103 side. It can be held securely.
- the bottom wall 150b of the guide passage 141b2 disposed below the axis O of the drive shaft 110 in the gravitational direction has a first space portion 141a and a guide passage 141b2 (that is, a second space).
- a small hole 150d (see FIGS. 5 and 6) that communicates with the portion 141b) is formed.
- the small hole 150b has an opening area and a height from the bottom of the first space 141a as a storage chamber so that an appropriate amount of oil is stored in the first space 141a.
- the pressure release passage 146 communicates the crank chamber 140 on the back of the piston 136 and the first space portion 141a to release the pressure in the crank chamber.
- the pressure release passage 146 is parallel to the drive shaft 110 in the cylinder block 101.
- the formed communication path 101c (see FIG. 1), the space 101d formed on the end side of the drive shaft 110 (see FIGS. 1 and 8), and the communication path formed on the end face of the cylinder block 101 on the cylinder head 104 side.
- 101e see FIG. 8
- communication holes not shown
- orifices 103c (see FIGS. 2 and 8) formed in the valve plate 103, and the discharge valve forming body 138, respectively.
- the formed communication hole 138b (see FIG. 3), the communication hole 139c (see FIG. 5) formed in the head gasket 139, and the end face of the protrusion 104d Is formed, and a first space portion 141a and communicated with by that groove 104e (see FIG. 8).
- the refrigerant gas containing the lubricating oil in the crank chamber 140 flows into the first space portion 141a via the pressure release passage 146.
- the pressure release passage 146 is connected to the first space portion 141a above the first space portion 141a in the gravity direction, for example, above the axis O of the drive shaft 110 in the gravity direction.
- the groove 104e of the pressure release passage 146 is connected to the first space portion 141a above the axis O of the drive shaft 110 in the gravity direction, and the groove 104e is connected to the partition wall 104b as shown in FIG. It is extended toward.
- variable capacity compressor 100 having the above configuration
- the lubricating oil is recirculated from the air conditioner system together with the refrigerant gas from the suction passage 104a, the lubricating oil is stored at the bottom of the first space portion 141a that is a storage chamber by its own weight and separated from the refrigerant gas. .
- the refrigerant gas from which the lubricating oil is separated is introduced into the second space 141b from the first space 141a through the communication hole 150a, and the refrigerant gas in the second space 141b is introduced through the suction hole 103a.
- the refrigerant gas is introduced into the cylinder bore 101a, and the refrigerant gas is compressed and discharged by the piston 136, thereby suppressing the outflow of the lubricating oil amount from the variable capacity compressor 100 to the vehicle air conditioner system.
- the lubricating oil stored in the crank chamber 140 flows into the first space portion 141a from the crank chamber 140 via the pressure release passage 146, the lubricating oil is similarly applied to the first space portion 141a by its own weight.
- the refrigerant gas from which the lubricating oil is separated from the communication hole 150a is introduced into the second space 141b, and the lubricating oil is prevented from flowing out into the second space 141b and thus to the external refrigerant circuit.
- the oil surface height of the lubricating oil stored in the first space 141a exceeds the small hole 150d, the lubricating oil flows back from the first space 141a to the second space 141b, and the variable capacity compressor This contributes to lubrication of 100 parts.
- the partition member 150 partitions the suction chamber 141 into the first space 141a and the second space 141b, and the suction passage 104a as the first space. 141a, the suction hole 103a is connected to the second space part 141b, and the refrigerant gas from which the lubricating oil is separated from the first space part 141a to the second space part 141b directly connected to the suction hole 103a is connected to the communication path 150a. Therefore, even if the lubricating oil recirculates together with the refrigerant gas from the air conditioner system and flows into the suction chamber 141, the refrigerant gas separated from the lubricating oil can be compressed and discharged.
- the pressure release passage 146 is connected to the first space portion 141a on the upstream side of the second space portion 141b, the lubricating oil is supplied from the crank chamber 140 to the suction chamber together with the refrigerant gas via the pressure release passage 146. Even if it flows out to 141, since the refrigerant gas from which the lubricating oil is separated is introduced from the first space portion to the second space portion through the communication path, the refrigerant gas from which the lubricating oil has been separated can be compressed and discharged. it can.
- the lubricating oil that has flowed out of the crank chamber is separated and stored in the first space portion, excessive lubricating oil is not stored in the crank chamber, and a decrease in oil viscosity during high-speed rotation can be suppressed. As a result, it is possible to reduce a risk that foreign matter stays in the crank chamber and abnormally wears the sliding portion inside the compressor.
- the high-temperature lubricating oil that has flowed out of the crank chamber 140 can be cooled by the refrigerant gas sucked from the suction passage 104a, and the decrease in the viscosity of the lubricating oil can be more reliably suppressed.
- the first space 141a not only stores lubricating oil, but also functions as a liquid storage space when the liquid refrigerant returns from the vehicle air conditioner system, and can reduce the risk of compressing the liquid refrigerant by the piston 136. .
- each suction hole 103a is partitioned by a forming wall (bottom wall 150b, side wall 150c) that forms the guide passage 141b2, the refrigerant gas can flow smoothly toward each suction hole 103a. Since the mutual interference of the suction refrigerant gas flowing toward the suction hole 103a can be prevented, the suction pressure pulsation level can be reduced.
- the pressure release passage 146 (groove 104e) is connected to the upper side in the gravity direction of the first space portion 141a, for example, the upper side in the gravity direction from the axis O of the drive shaft 110, the pressure release passage 146 is stored in the first space portion 141a. If the liquid level of the lubricating oil is, for example, located below the axis O of the drive shaft 110 in the direction of gravity, the refrigerant gas flowing from the crank chamber 140 toward the first space 141a causes the inside of the first space 141a. The stored lubricating oil is less likely to be agitated, and the stored oil splashes and can be prevented from flowing out from the communication hole 150a to the second space portion 141b, and further to the external refrigerant circuit. Can be reduced.
- the position of the communication path is adjusted simultaneously with the position adjustment of the partition member 150. Therefore, the position of the communication path can be easily adjusted.
- the two communication holes 150a are formed in FIG. 5, one may be sufficient and three or more may be sufficient.
- the communication path 150a which connects the 1st space part 141a and the 2nd space part 141b showed the case where it formed only by penetrating the partition member 150 in FIG. 6, it is not restricted to this, The 1st space part A cylindrical wall may protrude from the 141a side.
- the lubricating oil separation effect in the first space 141a can be further enhanced.
- the structure for improving the lubricating oil separation effect is not limited to the structure in which the communication path 150a is formed by the cylindrical wall, but may be another structure.
- the communication path (communication hole 150a) which connects the 1st space part 141a and the 2nd space part 141b was demonstrated in the case where it forms in the division member 150, it is not restricted to this, For example, it is another path by piping etc. May be provided.
- the partition member 150 is described as being integrally formed with the head gasket 139.
- the present invention is not limited to this, and the partition member 150 may be formed separately from the head gasket 139.
- the pressure relief passage 146 has been described in the case where it is connected to the first space portion 141a above the axis O of the drive shaft 110 in the gravity direction, the present invention is not limited to this, for example, the gravity direction from the axis O of the drive shaft 110 It may be connected to the first space portion 141a on the lower side so that the lubricating oil stored in the first space portion 141a can be returned to the crank chamber 140 side when the rotation of the variable capacity compressor 100 is stopped. .
- the small hole 150d is formed by communicating the first space 141a and the second space 141b.
- the small hole 150d is not limited thereto, and may be formed by communicating the first space 141a and the crank chamber 140. Good. In this way, when the rotation of the variable capacity compressor 100 is stopped, the lubricating oil stored in the first space 141a can be recirculated to the crank chamber 140 side.
- the compressor 100 can be a swing plate type variable capacity compressor in addition to a swash plate type variable capacity compressor.
- the present invention provides various known compressions such as a variable capacity compressor equipped with an electromagnetic clutch, a clutchless compressor without an electromagnetic clutch, a fixed capacity type reciprocating compressor, and a reciprocating compressor driven by a motor. Applicable to the machine.
- SYMBOLS 100 ... Compressor (variable capacity compressor), 103 ... Valve plate, 103a ... Suction hole, 104 ... Cylinder head, 104a ... Suction passage, 104d ... Projection part 136 ... Piston, 139 ... Head gasket, 140 ... Crank chamber, 141 ... suction chamber, 141a ... first space part, 141b ... second space part, 146 ... pressure release passage, 150 ... partition member, 150a ... communication passage (communication hole)
Abstract
Description
また、特許文献2に記載の圧縮機では、クランク室と吸入室とを連通する通路に遠心分離式のオイルセパレータを設ける構成であるため、構造か複雑になる。
このようにして、吸入室の一部である第1空間部を利用して潤滑オイルを分離することができるため、簡素な構造で、外部冷媒回路への潤滑オイルの流出を抑制して、OCRを低減することができる。
図1は、本発明が適用された圧縮機の一例である斜板式の可変容量圧縮機100の断面図である。この可変容量圧縮機100は、図示省略した冷媒回路(蒸発器及び凝縮器)に接続され、ピストン136を往復移動させ、当該冷媒回路から吸入した冷媒ガスを圧縮して吐出する。本実施形態において、可変容量圧縮機100は車両エアコンシステムに使用されるものとする。
制御弁300は、吐出室142とクランク室140とを連通する圧力供給通路145の開度を調整し、クランク室140への吐出ガス導入量を制御する。
また、クランク室140内の冷媒ガスは、放圧通路146(後に詳述する)を介して吸入室141(第1空間部141a)へ流れる。
また、放圧通路146は、第2空間部141bの上流側である第1空間部141aに接続されているため、放圧通路146を介して、潤滑オイルが冷媒ガスとともにクランク室140から吸入室141に流出したとしても、第1空間部から第2空間部に潤滑オイルを分離した冷媒ガスを、連通路を介して導入するので、潤滑オイルを分離した冷媒ガスを圧縮して吐出することができる。
このようにして、吸入室141の一部である第1空間部141aを利用して潤滑オイルを分離することができるため、簡素な構造で、外部冷媒回路への潤滑オイルの流出を抑制して、OCRを低減することができる。
本実施形態では、区画部材150は、ヘッドガスケット139に一体形成されている場合で説明したが、これに限らず、区画部材150をヘッドガスケット139と別体で形成してもよい。
Claims (6)
- ピストンを往復移動させ、吸入室から吸入孔を介して吸入した冷媒ガスを圧縮して吐出する圧縮機において、
吸入通路から冷媒ガスが流入する前記吸入室を、前記吸入通路と接続する第1空間部と、前記吸入孔と接続する第2空間部とに区画する区画部材と、
前記第1空間部と前記第2空間部とを連通し、潤滑オイルが分離された冷媒ガスを、前記第1空間部から前記第2空間部に導入する連通路と、
を備えて構成したことを特徴とする圧縮機。 - 前記ピストンの背方のクランク室と前記第1空間部とを連通してクランク室内の圧力を放出する放圧通路を更に備えた請求項1に記載の圧縮機。
- 前記吸入室が駆動軸の軸線の延長線上に配設される構成であって、
前記放圧通路は、前記駆動軸の軸線より重力方向上側で接続していることを特徴とする請求項2に記載の圧縮機。 - 前記連通路は、前記区画部材に形成されていることを特徴とする請求項1~3のいずれか1つに記載の圧縮機。
- 前記区画部材は、前記吸入孔が形成されたバルブプレートと、前記吸入室が形成されたシリンダヘッドとの間に介在させたヘッドガスケットの前記吸入室に面した部分を、前記吸入室内に突出させて形成したことを特徴とする請求項1~4のいずれか1つに記載の圧縮機。
- 前記バルブプレートに面した前記シリンダヘッドの吸入室形成壁面に前記ヘッドガスケットの区画部材部分の周縁部を前記バルブプレート側に押圧する突起部を突設したことを特徴とする請求項5に記載の圧縮機。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112013005321.7T DE112013005321B4 (de) | 2012-11-07 | 2013-11-07 | Kompressor |
US14/441,118 US9797638B2 (en) | 2012-11-07 | 2013-11-07 | Compressor |
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Application Number | Priority Date | Filing Date | Title |
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JP2012245724A JP6097051B2 (ja) | 2012-11-07 | 2012-11-07 | 圧縮機 |
JP2012-245724 | 2012-11-07 |
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WO2014073620A1 true WO2014073620A1 (ja) | 2014-05-15 |
Family
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PCT/JP2013/080161 WO2014073620A1 (ja) | 2012-11-07 | 2013-11-07 | 圧縮機 |
Country Status (4)
Country | Link |
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US (1) | US9797638B2 (ja) |
JP (1) | JP6097051B2 (ja) |
DE (1) | DE112013005321B4 (ja) |
WO (1) | WO2014073620A1 (ja) |
Families Citing this family (2)
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JP6540954B2 (ja) * | 2015-07-02 | 2019-07-10 | サンデン・オートモーティブコンポーネント株式会社 | 圧縮機 |
KR20200072080A (ko) * | 2018-12-12 | 2020-06-22 | 한온시스템 주식회사 | 사판식 압축기 |
Citations (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 (ja) * | 1991-03-05 | 1992-10-01 | Matsushita Electric Ind Co Ltd | コンプレッサ |
JPH0596473U (ja) * | 1992-06-01 | 1993-12-27 | 株式会社豊田自動織機製作所 | ピストン型圧縮機 |
JP2002213350A (ja) * | 2000-11-17 | 2002-07-31 | Toyota Industries Corp | 容量可変型圧縮機 |
JP2006077737A (ja) * | 2004-09-13 | 2006-03-23 | Valeo Thermal Systems Japan Corp | 圧縮機 |
JP2012127233A (ja) * | 2010-12-14 | 2012-07-05 | Sanden Corp | 可変容量圧縮機 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51105608A (ja) * | 1975-03-13 | 1976-09-18 | Sentoraru Jidosha Kogyo Kk | |
US4392788A (en) * | 1980-08-15 | 1983-07-12 | Diesel Kiki Co., Ltd. | Swash-plate type compressor having oil separating function |
JPH07332239A (ja) * | 1994-06-03 | 1995-12-22 | Toyota Autom Loom Works Ltd | 往復動型圧縮機 |
EP2000672B1 (en) * | 2006-03-29 | 2015-05-06 | Kabushiki Kaisha Toyota Jidoshokki | Compressor |
-
2012
- 2012-11-07 JP JP2012245724A patent/JP6097051B2/ja not_active Expired - Fee Related
-
2013
- 2013-11-07 DE DE112013005321.7T patent/DE112013005321B4/de not_active Expired - Fee Related
- 2013-11-07 WO PCT/JP2013/080161 patent/WO2014073620A1/ja active Application Filing
- 2013-11-07 US US14/441,118 patent/US9797638B2/en not_active Expired - Fee Related
Patent Citations (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 (ja) * | 1991-03-05 | 1992-10-01 | Matsushita Electric Ind Co Ltd | コンプレッサ |
JPH0596473U (ja) * | 1992-06-01 | 1993-12-27 | 株式会社豊田自動織機製作所 | ピストン型圧縮機 |
JP2002213350A (ja) * | 2000-11-17 | 2002-07-31 | Toyota Industries Corp | 容量可変型圧縮機 |
JP2006077737A (ja) * | 2004-09-13 | 2006-03-23 | Valeo Thermal Systems Japan Corp | 圧縮機 |
JP2012127233A (ja) * | 2010-12-14 | 2012-07-05 | Sanden Corp | 可変容量圧縮機 |
Also Published As
Publication number | Publication date |
---|---|
DE112013005321B4 (de) | 2019-11-14 |
JP6097051B2 (ja) | 2017-03-15 |
DE112013005321T5 (de) | 2015-09-10 |
US9797638B2 (en) | 2017-10-24 |
JP2014095301A (ja) | 2014-05-22 |
US20150300711A1 (en) | 2015-10-22 |
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