WO2012081356A1 - 可変容量圧縮機 - Google Patents

可変容量圧縮機 Download PDF

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Publication number
WO2012081356A1
WO2012081356A1 PCT/JP2011/076633 JP2011076633W WO2012081356A1 WO 2012081356 A1 WO2012081356 A1 WO 2012081356A1 JP 2011076633 W JP2011076633 W JP 2011076633W WO 2012081356 A1 WO2012081356 A1 WO 2012081356A1
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WO
WIPO (PCT)
Prior art keywords
discharge
pressure
pressure relief
passage
chamber
Prior art date
Application number
PCT/JP2011/076633
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
田口　幸彦
Original Assignee
サンデン株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by サンデン株式会社 filed Critical サンデン株式会社
Priority to CN201180059813.2A priority Critical patent/CN103261687B/zh
Priority to US13/993,588 priority patent/US20130259714A1/en
Priority to DE112011104374.0T priority patent/DE112011104374B4/de
Publication of WO2012081356A1 publication Critical patent/WO2012081356A1/ja

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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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes

Definitions

  • the present invention relates to a compressor, and more particularly to a variable capacity compressor used in a vehicle air conditioner system.
  • Patent Document 1 in a swash plate type variable capacity compressor constituting a refrigerant circuit, a relief valve is provided in a communication path that connects a discharge chamber and a crank chamber, and when the pressure in the discharge chamber exceeds a predetermined value. Describes that the relief valve opens.
  • Patent Document 2 in a refrigerant circuit provided with a swash plate type variable capacity compressor, a check valve is provided in a high pressure passage between a condenser and a discharge chamber of the compressor, and a check valve in the high pressure passage is provided. It is described that a relief valve is provided upstream.
  • the region of the refrigerant circuit where the discharge pressure of the compressor acts may become abnormally high.
  • the control for shutting off the electromagnetic clutch connected to the drive shaft of the compressor is executed, or the control for setting the discharge capacity of the compressor to the minimum discharge capacity is executed, and the discharge pressure region is controlled. By reducing the pressure, an abnormally high pressure in the discharge pressure region is avoided.
  • the relief valves described in Patent Documents 1 and 2 must avoid abnormally high pressure in the discharge pressure region by operating mechanically even if the electrical control as described above does not function.
  • the technique described in Patent Document 1 when the pressure in the discharge pressure region becomes abnormally high, the refrigerant in the discharge pressure region can be discharged into the crank chamber without being discharged into the atmosphere.
  • some variable displacement compressors used in a vehicle air conditioner system include a check valve in a discharge pressure region as described in Patent Document 2.
  • variable capacity compressor has a plurality of cylinder bores formed in parallel with each other around the axis, a crank chamber in the front, a suction chamber and a discharge chamber in the rear, and a discharge chamber and a discharge side outside.
  • a conversion mechanism including a piston that discharges into the discharge chamber, a drive shaft that is rotatably supported in the housing, and a swash plate that is disposed in the crank chamber and converts the rotational motion of the drive shaft into reciprocating motion of the piston.
  • a displacement control valve that changes the stroke of the reciprocating motion of the piston by changing the tilt angle of the swash plate by controlling the pressure in the crank chamber.
  • the housing includes a first pressure relief passage branched from the discharge passage and connected to the crank chamber, and a second pressure relief passage connecting the crank chamber and the suction chamber.
  • a check valve that suppresses the backflow of the refrigerant from the discharge-side external refrigerant circuit to the discharge chamber is provided upstream of the branch position of the discharge passage with the first pressure release passage.
  • the first pressure relief passage is provided with a high pressure relief valve that opens the first pressure relief passage when the pressure downstream of the check valve in the discharge passage exceeds a predetermined value.
  • the first pressure release passage is opened by the high pressure relief valve, and the high pressure refrigerant flows into the first pressure release passage. Therefore, the refrigerant is not released to the atmosphere at the time of depressurization.
  • the refrigerant in this region is discharged to the crank chamber through the first pressure release passage.
  • the second pressure release passage for example, when the pressure of the discharge-side external refrigerant circuit becomes abnormally high, the high-pressure refrigerant is discharged downstream from the check valve. Since it can be smoothly moved to the suction chamber via the passage, the high pressure relief valve, the first pressure release passage, the crank chamber, and the second pressure release passage, an abnormal high pressure in the discharge-side external refrigerant circuit can be avoided. it can.
  • Sectional view of a variable displacement compressor according to a first embodiment of the present invention Fragmentary cross-sectional view of a variable displacement compressor according to the exemplary embodiment
  • Cross-sectional view of a high pressure relief valve according to the exemplary embodiment Sectional drawing of the variable capacity compressor in the 2nd Embodiment of this invention
  • Sectional view of the low-pressure relief valve in the high frequency embodiments Sectional drawing of the principal part of the variable capacity compressor in the 3rd Embodiment of this invention.
  • Cross-sectional view of a high pressure relief valve according to the exemplary embodiment Sectional drawing of the principal part of the variable capacity compressor in the 4th Embodiment of this invention
  • FIG. 1 shows a schematic configuration of a variable capacity compressor according to a first embodiment of the present invention.
  • a variable capacity compressor 100 used in a vehicle air conditioner system includes a cylinder block 101, a front housing 102 provided at one end of the cylinder block 101, and a cylinder provided at the other end of the cylinder block 101 via a valve plate 103. And a head 104.
  • a plurality of cylinder bores 101a are formed in parallel to each other around the axis (around the drive shaft 106).
  • a drive shaft 106 is provided so as to traverse the crank chamber 105 defined by the cylinder block 101 and the front housing 102 and located in front of the cylinder bore 101a.
  • a swash plate 107 is provided around the center of the drive shaft 106. Has been placed. The swash plate 107 is coupled via a rotor 108 fixed to the drive shaft 106 and a connecting portion 109, and is supported by the drive shaft 106 so that the tilt angle is variable.
  • a coil spring 110 is mounted between the rotor 108 and the swash plate 107 to urge the swash plate 107 toward the minimum tilt angle, and on the opposite side of the swash plate 107, the tilt angle of the swash plate 107 is increased.
  • a coil spring 111 that is biased toward the end is mounted.
  • One end of the drive shaft 106 extends through the inside of the boss portion 102a protruding to the outside of the front housing 102, and is connected to a power transmission device (not shown).
  • a power transmission device (not shown)
  • power from an external drive source (not shown) is transmitted to the power transmission device.
  • a shaft seal device 112 is inserted between the drive shaft 106 and the boss portion 102a, thereby blocking the inside and the outside of the variable capacity compressor 100.
  • the drive shaft 106 is supported by bearings 113, 114, 115, and 116 in the radial direction and the thrust direction, and is rotatable in synchronization with the rotation of the power transmission device.
  • a piston 117 is inserted into the cylinder bore 101a, and the periphery of the outer periphery of the swash plate 107 is accommodated in a recess 117a at one end inside the piston 117.
  • the piston 117 and the swash plate 107 are connected to each other via a shoe 118. It has a structure that works together. Accordingly, the piston 117 can reciprocate in the cylinder bore 101a by the rotation of the drive shaft 106.
  • the function of the conversion mechanism in the present invention is realized by the swash plate 107, the rotor 108, the connecting portion 109, the coil springs 110 and 111, and the shoe 118.
  • a suction chamber 119 is formed at the center, and a discharge chamber 120 is formed so as to surround the suction chamber 119 in an annular shape.
  • the discharge chamber 120 is annularly arranged in the cylinder head 104 on the outer side in the radial direction of the suction chamber 119.
  • the suction chamber 119 and the discharge chamber 120 are located behind the cylinder bore 101a.
  • the suction chamber 119 communicates with the cylinder bore 101a through a communication hole 103a provided in the valve plate 103 and a suction valve (not shown).
  • the discharge chamber 120 communicates with the cylinder bore 101a via a discharge valve (not shown) and a communication hole 103b provided in the valve plate 103.
  • the piston 117 that reciprocates in the cylinder bore 101 a compresses the refrigerant (for example, refrigerant gas) sucked from the suction chamber 119 and discharges it into the discharge chamber 120.
  • the front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 140 via a gasket (not shown) to form a housing.
  • the housing in the present invention includes the front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104.
  • a muffler 121 having an expansion space for reducing noise and vibration due to refrigerant pulsation is provided on the upper portion of the cylinder block 101.
  • a forming wall 101b erected on the upper surface of the cylinder block 101 and a box-shaped lid member 122 having a lower surface opening that forms a part of the housing described above are bolted together via a seal member (not shown). Is formed.
  • the formation wall 101b corresponds to “a volume portion formed by providing a recess on the outer surface of the cylinder block” in the present invention.
  • the lid member 122 covers the opening of the volume portion.
  • a discharge port 122 a that communicates the inside and the outside is formed at the upper end of the lid member 122.
  • a check valve 200 is disposed in a muffler space 123 that is a space in the muffler 121 (that is, the above-described expansion space).
  • the check valve 200 is disposed at a connection portion between the communication passage 124 communicating with the discharge chamber 120 and the muffler space 123.
  • the check valve 200 operates in response to a pressure difference between the communication path 124 (upstream side) and the muffler space 123 (downstream side), and shuts off the communication path 124 when the pressure difference is smaller than a predetermined value. When the pressure difference is larger than a predetermined value, the communication path 124 is opened.
  • the predetermined value is a threshold value for switching opening and closing of the check valve 200 and is set in advance so as to suppress the back flow of the refrigerant from the muffler space 123 (downstream side) to the communication path 124 (upstream side). ing.
  • the discharge chamber 120 is connected to the discharge side refrigerant circuit of the vehicle air conditioner system (the discharge side external refrigerant in the present invention) via the discharge passage constituted by the communication passage 124, the check valve 200, the muffler space 123, and the discharge port 122a. Circuit). Further, the check valve 200 suppresses the back flow of the refrigerant from the discharge side refrigerant circuit to the discharge chamber 120.
  • the cylinder head 104 is formed with a suction port 104a and a communication path 104b that connects the suction port 104a and the suction chamber 119.
  • the suction chamber 119 is connected to the suction side refrigerant circuit (suction side external refrigerant circuit in the present invention) of the vehicle air conditioner system via the suction passage constituted by the suction port 104a and the communication passage 104b.
  • the cylinder head 104 is provided with a capacity control valve 300.
  • the capacity control valve 300 controls the amount of refrigerant introduced into the crank chamber 105 by adjusting the opening of the air supply passage 125 that connects the discharge chamber 120 and the crank chamber 105. Further, the refrigerant in the crank chamber 105 passes through the gaps between the bearings 115 and 116 and the drive shaft 106, and is extracted via the space 127 formed in the cylinder block 101 and the orifice 103 c formed in the valve plate 103. It flows into the suction chamber 119 via the passage 128.
  • the capacity control valve 300 is an external control type capacity control valve operated by an external signal. Specifically, the capacity control valve 300 senses the pressure of the suction chamber 119 via the communication passage 126 communicating with the suction chamber 119, and adjusts the energization amount to the solenoid of the capacity control valve 300 according to the result. Thus, the discharge capacity of the variable capacity compressor 100 is controlled so that the pressure in the suction chamber 119 becomes a predetermined value.
  • FIG. 2 shows a cross section of the main part of the variable capacity compressor 100 in the present embodiment.
  • the cross section of the variable capacity compressor 100 shown in FIG. 2 is at a position where the upper part thereof is rotated slightly to the front side of the paper surface around the drive shaft 106 from the cross section of the variable capacity compressor 100 shown in FIG.
  • the cross section of the variable capacity compressor 100 is shown.
  • communication passages 101 c and 101 d that connect the muffler space 123 and the crank chamber 105 are formed downstream of the check valve 200 in the muffler space 123.
  • the communication path 101c communicates the muffler space 123 and the communication path 101d.
  • the communication passage 101 d is formed as a part of an insertion hole through which the through bolt 140 is inserted, and communicates with the crank chamber 105.
  • a large flow path area is secured in a portion of the insertion hole that functions as the communication path 101d.
  • a high-pressure relief valve 250 is disposed at a connection position with the communication path 101 c in the muffler space 123.
  • the muffler space 123 can communicate with the crank chamber 105 via the internal passage (including a space 256 described later) of the high-pressure relief valve 250, the communication passage 101c, and the communication passage 101d.
  • the internal passage, the communication passage 101 c, and the communication passage 101 d of the high-pressure relief valve 250 function as a first pressure release passage that connects the discharge passage and the crank chamber 105. Therefore, the first pressure release passage branches from the discharge passage downstream of the check valve 200 in the discharge passage and is connected to the crank chamber 105.
  • the first pressure relief passage is located radially outward from the cylinder bore 101a when viewed from the drive shaft 106.
  • FIG. 3 shows a schematic configuration of the high-pressure relief valve 250.
  • the high-pressure relief valve 250 receives a bottomed cylindrical valve housing 251, a valve body 252 disposed in the valve housing 251, a spring 253 that biases the valve body 252 in the valve closing direction, and one end of the spring 253.
  • a spring guide 254 and an O-ring 255 are included.
  • An inlet hole 251 a that communicates the inside and the outside of the valve housing 251 is formed at the upper end of the valve housing 251.
  • An outlet hole 254 a that communicates the inside and the outside of the valve housing 251 is formed at the center of the spring guide 254.
  • the pressure of the crank chamber 105 acts on a space 256 on the back side of the valve body 242 defined by the valve housing 251 and the spring guide 254. Therefore, the high pressure relief valve 250 opens when the pressure in the muffler space 123 (discharge pressure region) exceeds a predetermined value set in advance based on the pressure in the crank chamber 105 and the biasing force of the spring 253, The refrigerant in the muffler space 123 is discharged to the crank chamber 105 through the first pressure release passage.
  • the high pressure relief valve 250 opens the first pressure relief passage when the pressure downstream of the check valve 200 in the discharge passage exceeds a predetermined value.
  • the predetermined value is a threshold value for switching the opening and closing of the high pressure relief valve 250, and is set in advance to a pressure higher than the pressure that can occur in a normal air conditioner use state. The valve is closed when the air conditioner is in use.
  • the high-pressure relief valve 250 is arranged so that one end side where the O-ring 255 is mounted is fitted into the cylinder block 101 and the other end side faces the lid member 122.
  • the high pressure relief valve 250 is held on the cylinder block 101 by the elastic force of the O-ring 255. Further, in order to prevent the high pressure relief valve 250 from coming off from the fitting portion of the cylinder block 101, a part of the lid member 122 comes into contact with the upper surface of the flange portion 251b of the valve housing 251, and the movement of the high pressure relief valve 250 is prevented. Being regulated.
  • the high pressure relief valve 250 When the variable capacity compressor 100 is operated and the refrigerant is circulating in the refrigerant circuit of the vehicle air conditioner system (the check valve 200 is opened), the pressure in the discharge pressure region becomes abnormally high, and the pressure in the muffler space 123 is When a predetermined value set in advance based on the pressure in the crank chamber 105 and the biasing force of the spring 253 is exceeded, the high-pressure relief valve 250 is opened, and the refrigerant in the muffler space 123 passes through the first pressure release passage. And discharged into the crank chamber 105.
  • the pressure in the crank chamber 105 rises rapidly, the pressure difference between the crank chamber 105 and the suction chamber 119 increases, the inclination angle of the swash plate 107 decreases, and the stroke of the reciprocating motion of the piston 117 decreases, so that variable displacement compression is achieved. Since the discharge capacity of the machine 100 becomes the minimum discharge capacity, the pressure in the discharge chamber 120 is greatly reduced and the abnormal high pressure of the variable capacity compressor 100 is avoided. At this time, the check valve 200 is closed, but since the muffler space 123 is downstream of the check valve 200, the refrigerant in the discharge side refrigerant circuit of the vehicle air conditioner system passes through the first pressure release passage to the crank chamber 105.
  • the air flows into the suction chamber 119 via the extraction passage 128.
  • the bleed passage 128 functions as a second pressure relief passage in the present invention. In this way, not only is the abnormal high pressure in the discharge chamber 120 of the variable capacity compressor 100 (ie, upstream of the check valve 200 in the discharge pressure region) avoided, but also the discharge side refrigerant circuit (ie, discharge) of the vehicle air conditioner system. An abnormally high pressure in the pressure region downstream of the check valve 200 can also be avoided.
  • the high pressure relief valve 250 is closed and the vehicle air conditioner system shifts to a normal operation state.
  • the high pressure relief valve 250 causes the first pressure relief passage (the internal passage of the high pressure relief valve 250, the communication passage 101c, and the communication passage 101d). Since the open and high-pressure refrigerant is discharged to the crank chamber 105 through the first pressure release passage, it is not necessary to release the refrigerant to the atmosphere during pressure release.
  • the refrigerant downstream from the check valve 200 in the discharge passage passes through the first pressure release passage (the internal passage of the high pressure relief valve 250, the communication passage). It is discharged into the crank chamber 105 through the passage 101c and the communication passage 101d).
  • the pressure in the crank chamber 105 rises rapidly, the discharge capacity of the variable capacity compressor 100 instantaneously shifts to the minimum discharge capacity, and the pressure in the discharge chamber 120 is greatly reduced, so that an abnormally high pressure in the discharge chamber 120 is avoided. be able to.
  • the first pressure release passage the internal passage of the high-pressure relief valve 250, the communication passage 101c, and the communication passage 101d
  • the second pressure release passage bleeding passage 128, for example.
  • the abnormally high pressure in the discharge chamber 120 of the variable capacity compressor 100 that is, upstream from the check valve 200 in the discharge pressure region
  • the discharge-side external refrigerant circuit that is, the check in the discharge pressure region
  • the first pressure release passage (the internal passage of the high pressure relief valve 250, the communication passage 101c, and the communication passage 101d) is more radially outward than the cylinder bore 101a when viewed from the drive shaft 106. It is located in the direction.
  • the communication passages 101c and 101d used to connect the muffler space 123 and the crank chamber 105 can be formed relatively easily, and the high-pressure relief valve 250 can be disposed relatively easily. the variable displacement compressor 100 can be efficiently manufactured.
  • the muffler 121 having an expansion space is provided between the communication passage 124 and the discharge port 122a, and the high-pressure relief valve 250 is disposed in the expansion space (muffler space 123). .
  • the muffler 121 can function as a cover for the high-pressure relief valve 250, damage to the high-pressure relief valve 250 from the outside can be reduced.
  • the muffler 121 is formed by a volume part (formation wall 101b) formed by providing a recess on the upper surface of the cylinder block 101, and a lid member 122 that covers the opening of the volume part.
  • a part of the insertion hole through which the through bolt 140 is inserted functions as the communication path 101d that constitutes the first pressure release path.
  • FIG. 4 shows a schematic configuration of a variable capacity compressor in the second embodiment of the present invention. Differences from the first embodiment shown in FIGS. 1 to 3 will be described.
  • the extraction passage 128 includes the orifice 103c.
  • the extraction passage 128 includes a low-pressure relief valve 280 instead of the orifice 103c.
  • FIG. 5 shows a schematic configuration of the low pressure relief valve 280.
  • the low pressure relief valve 280 is disposed in the suction chamber 119 and includes a valve seat forming member 281, a valve body 282, a spring 283, and a valve housing 284.
  • the valve seat forming member 281 is formed with an inlet hole 281a communicating with the crank chamber 105 via a space 127 and the like, and a valve seat 281b.
  • valve seat forming member 281 has a flange 281c.
  • the flange 281 c is fitted into a through-hole formed in the valve plate 103 in advance, and is sandwiched and held between the intake valve forming body 150 and the discharge valve forming body 160 disposed adjacent to the valve plate 103.
  • the valve body 282 has a seal surface that is seated on the valve seat 281b and closes the inlet hole 281a, and a cylindrical outer peripheral surface.
  • the valve body 282 is formed with an orifice 282a so that the crank chamber 105 and the suction chamber 119 are always in communication when the valve body 282 is seated on the valve seat 281b.
  • the spring 283 biases the valve body 282 toward the valve seat 281b.
  • the valve housing 284 has a bottomed cylindrical shape, and receives one end of the spring 283 on the inside thereof, and supports the cylindrical outer peripheral surface of the valve body 282 in a slidable manner.
  • the valve housing 284 includes a plurality of outlet holes 284 a that are formed through the cylindrical peripheral surface and communicate with the suction chamber 119.
  • a communication hole 284 b is formed in the valve housing 284 so that the pressure of the suction chamber 119 acts on the space 285 on the back side of the valve body 282. Therefore, the low pressure relief valve 280 opens when the pressure difference between the crank chamber 105 and the suction chamber 119 exceeds a predetermined value set in advance based on the biasing force of the spring 283, and the refrigerant in the crank chamber 105 is extracted. A large amount is discharged to the suction chamber 119 through the passage 128 (second pressure relief passage).
  • the predetermined value is a threshold value for switching opening and closing of the low pressure relief valve 280, and a value larger than the pressure difference between the crank chamber 105 and the suction chamber 119 generated in the normal pressure control of the crank chamber 105 is set in advance. Therefore, the low-pressure relief valve 280 is closed in a normal air conditioner use state.
  • the operation of the high pressure relief valve 250 and the low pressure relief valve 280 in this embodiment will be described.
  • the check valve 200 When the variable capacity compressor 100 is operated and the refrigerant is circulating in the refrigerant circuit of the vehicle air conditioner system (the check valve 200 is opened), the pressure in the discharge pressure region becomes abnormally high, and the pressure in the muffler space 123 is When a predetermined value set in advance based on the pressure in the crank chamber 105 and the biasing force of the spring 253 is exceeded, the high-pressure relief valve 250 is opened, and the refrigerant in the muffler space 123 passes through the first pressure relief passage. And discharged into the crank chamber 105.
  • the pressure in the crank chamber 105 increases rapidly, the pressure difference between the crank chamber 105 and the suction chamber 119 increases, the inclination angle of the swash plate 107 decreases, the stroke of the reciprocating motion of the piston 117 decreases, and variable displacement compression is performed. Since the discharge capacity of the machine 100 becomes the minimum discharge capacity, the pressure in the discharge chamber 120 is greatly reduced and the abnormal high pressure of the variable capacity compressor 100 is avoided.
  • the low pressure relief valve 280 is opened, and the refrigerant in the crank chamber 105 is extracted. It is discharged to the suction chamber 119 through the passage 128 (second pressure relief passage).
  • the check valve 200 is closed, but since the muffler space 123 is downstream of the check valve 200, the refrigerant in the discharge side refrigerant circuit of the vehicle air conditioner system continuously flows into the crank chamber 105, and the extraction passage It moves to the suction chamber 119 via 128 (second pressure relief passage).
  • the second pressure relief passage (bleeding passage 128) includes a low pressure relief valve that opens the second pressure relief passage when the pressure difference between the crank chamber 105 and the suction chamber 119 exceeds a predetermined value. 280 is provided.
  • a large amount of refrigerant can be moved to the suction chamber 119 while suppressing an excessive increase in the pressure difference between the crank chamber 105 and the suction chamber 119, so that the abnormal high pressure in the discharge pressure region can be quickly eliminated. can do.
  • the passage functioning as the second pressure release passage is only the extraction passage 128, but the second pressure release passage is not limited to this, and for example, separately from the extraction passage 128, the low pressure relief valve 280 is provided. It may be provided a new second pressure release passage comprises a. That is, the second pressure release passage may be a plurality.
  • FIG. 6 shows a schematic configuration of a variable capacity compressor in the third embodiment of the present invention.
  • FIG. 7 shows a schematic configuration of the high-pressure relief valve in the present embodiment. Differences from the first embodiment shown in FIGS. 1 to 3 will be described.
  • the high pressure relief valve 250 opens when the pressure in the muffler space 123 (discharge pressure region) exceeds a predetermined value set in advance based on the pressure in the crank chamber 105 and the biasing force of the spring 253.
  • the high-pressure relief valve 260 opens when the pressure in the muffler space 123 (discharge pressure region) exceeds a predetermined value set in advance based on the biasing force of the spring 263. It is a structure to do.
  • the high pressure relief valve 260 includes a valve housing 261, a diaphragm 262, a spring 263, a spring guide 264 disposed between the diaphragm 262 and one end of the spring 263, and the other end of the spring 263 and the valve housing 261.
  • a spring guide 265 and an O-ring 266 are provided.
  • the valve housing 261 includes a first housing member 261a constituting one end side thereof and a second housing member 261b constituting the other end side thereof.
  • the first housing member 261a is formed with an inlet hole 261c communicating with the muffler space 123, an outlet hole 261d communicating with the crank chamber 105 via the communication passages 101c and 101d, and a valve seat 261e on which the diaphragm 262 is seated. ing.
  • One end surface of the diaphragm 262 receives the pressure of the muffler space 123.
  • a space defined by the diaphragm 262 and the second housing member 261b of the valve housing 261 is maintained at a negative pressure, and the spring 263 biases the diaphragm 262 in the valve seat direction.
  • the high-pressure relief valve 260 opens and closes when the diaphragm 262 that is displaced in response to the pressure in the muffler space 123 (discharge pressure region) is seated on and separated from the valve seat 261e. ) Exceeds a predetermined value, the valve is opened, and the refrigerant in the muffler space 123 is discharged to the crank chamber 105 through the first pressure release passage.
  • the first housing member 261a and the second housing member 261b of the valve housing 261 are joined together by welding the two flange portions 261f with the diaphragm 262 sandwiched therebetween.
  • the first housing member 261a and the second housing member 261b are formed of the same type of material (for example, a stainless steel material).
  • the high pressure relief valve 260 has one end side (first housing member 261 a) on which the O-ring 266 is mounted fitted into the cylinder block 101 and the other end side (second housing member 261 b) faces the lid member 122. It is arranged.
  • the high pressure relief valve 260 is held on the cylinder block 101 by the elastic force of the O-ring 266. Further, in order to prevent the high pressure relief valve 260 from coming off from the fitting portion of the cylinder block 101, a part of the lid member 122 is in contact with the upper surface of the flange portion 261 f of the valve housing 261. That is, the high pressure relief valve 260 is sandwiched between the cylinder block 101 and the lid member 122 at the flange portion 261 f of the valve housing 261.
  • the high pressure relief valve 260 has a structure that opens when the pressure in the muffler space 123 (discharge pressure region) exceeds a predetermined value set in advance based on the biasing force of the spring 263.
  • the variable capacity compressor 100 and this compressor are used because they can operate in response to the pressure in the muffler space 123 (discharge pressure region) without being relatively affected by the pressure in the crank chamber 105. it is possible to improve the reliability of the vehicle air-conditioning system.
  • the high pressure relief valve 260 is sandwiched between the cylinder block 101 and the lid member 122. This eliminates the need for a fixing member for fixing the high-pressure relief valve 260 to the cylinder block 101, thereby realizing improved mounting properties and cost reduction.
  • the diaphragm 262 is used as the pressure sensitive member.
  • the pressure sensitive member is not limited to this, and for example, a bellows may be used as the pressure sensitive member.
  • the high-pressure relief valve 260 has the diaphragm 262 function as a valve body.
  • the high-pressure relief valve 260 is not limited to the diaphragm 262.
  • the high-pressure relief valve 260 can be used together with the diaphragm 262 or the diaphragm. It may replace with 262 and you may comprise so that a valve body may be provided.
  • FIG. 8 shows a schematic configuration of a variable capacity compressor in the fourth embodiment of the present invention. Differences from the first embodiment shown in FIGS. 1 to 3 will be described.
  • the muffler 121 is formed on the outer peripheral portion of the cylinder block 101, but in the fourth embodiment, the muffler 121 is not formed.
  • the cylinder head 104 includes a discharge port 104c, a communication passage 104d extending outward from the discharge chamber 120 toward the discharge port 104c, and extending perpendicularly to the axial direction of the drive shaft 106. It is equipped with.
  • the function of the discharge passage in the present invention is realized by the discharge port 104c and the communication passage 104d.
  • a check valve 200 is provided in the middle of the communication path 104d.
  • the cylinder head 104 is formed with a part of a communication path 130 that communicates with the communication path 104 d downstream of the check valve 200.
  • the communication path 130 branches from the downstream side of the check valve 200 in the communication path 104 d of the cylinder head 104 and extends in parallel with the drive shaft 106, and is connected to the high-pressure relief valve 270 provided in the cylinder block 101 via the valve plate 103. It communicates with the inlet hole.
  • the high pressure relief valve 270 has one end on which an O-ring is mounted fitted into the cylinder block 101 and the other end protruding outward from the cylinder block 101.
  • the high-pressure relief valve 270 has the same configuration as the high-pressure relief valve 260, but protrudes outward from the cylinder block 101. Therefore, an O-ring for sealing the atmosphere side is added, The snap ring 132 prevents it from coming off.
  • the outlet hole of the high-pressure relief valve 270 communicates with the crank chamber 105 through the communication passages 101c and 101d. Therefore, the first pressure relief passage that communicates the communication passage 104d and the crank chamber 105 is constituted by the communication passage 130, the internal passage of the high-pressure relief valve 270, and the communication passages 101c and 101d.
  • the communication passage 130 branches from the downstream side of the check valve 200 in the communication passage 104 d of the cylinder head 104 and extends in parallel with the drive shaft 106, and is connected to the cylinder block 101 via the valve plate 103. Since it communicates with the inlet hole of the high-pressure relief valve 270 provided, the communication path 130 can be easily formed as in the case of forming the insertion hole for the through bolt 140.
  • the outlet hole of the high pressure relief valve is connected to the crank chamber 105 via a part of the insertion hole for the through bolt 140 (communication path 101d).
  • the crank chamber 105 may be directly connected without the insertion hole for the through bolt 140.
  • the upstream side of the high pressure relief valve in the first pressure release passage, or the discharge side refrigerant circuit side from the branch position of the discharge passage with the first pressure release passage It is possible to arrange a filter. Thereby, when the high-pressure relief valve is opened, foreign matter in the discharge side refrigerant circuit can be captured by the filter, so that it is possible to reduce the risk of durability deterioration due to the foreign matter.
  • variable capacity compressor 100 has the discharge chamber 120 arranged annularly outside the suction chamber 119 in the radial direction.
  • the arrangement of the discharge chamber is not limited to this, and for example, the arrangement of the discharge chamber and the suction chamber is reversed from that of the first to fourth embodiments described above, and the suction chamber is arranged annularly outside the discharge chamber in the radial direction. You may be made to do.
  • the low-pressure relief valve 280 is disposed in the suction chamber 119.
  • the discharge chamber and the suction chamber are disposed in the opposite direction to the above-described second embodiment.
  • the low pressure relief valve 280 is preferably disposed on the cylinder block 101 side.
  • variable capacity compressor 100 in the first to fourth embodiments described above may be a variable capacity compressor provided with an electromagnetic clutch, a clutchless compressor, or the like.
  • the external drive source that drives the variable capacity compressor 100 may be a vehicle engine, a motor, or the like.
  • variable capacity compressor 100 in the first to fourth embodiments described above has a configuration in which the refrigerant is discharged into the crank chamber 105 without being discharged into the atmosphere when an abnormally high pressure in the discharge pressure region is avoided. Therefore, this configuration is particularly suitable for a variable capacity compressor that uses a combustible refrigerant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
PCT/JP2011/076633 2010-12-14 2011-11-18 可変容量圧縮機 WO2012081356A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201180059813.2A CN103261687B (zh) 2010-12-14 2011-11-18 可变容量压缩机
US13/993,588 US20130259714A1 (en) 2010-12-14 2011-11-18 Variable Displacement Compressor
DE112011104374.0T DE112011104374B4 (de) 2010-12-14 2011-11-18 Kompressor mit variabler Verdrängung und Hochdruckentlastungsventil

Applications Claiming Priority (2)

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JP2010-278312 2010-12-14
JP2010278312A JP5697022B2 (ja) 2010-12-14 2010-12-14 可変容量圧縮機

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JP5414115B2 (ja) * 2010-01-21 2014-02-12 サンデン株式会社 可変容量型圧縮機の容量検出装置およびそれを備えた可変容量型圧縮機
JP6097051B2 (ja) * 2012-11-07 2017-03-15 サンデンホールディングス株式会社 圧縮機
JP2014095320A (ja) * 2012-11-08 2014-05-22 Sanden Corp 圧縮機
JP6005483B2 (ja) * 2012-11-08 2016-10-12 サンデンホールディングス株式会社 可変容量圧縮機
JP6192369B2 (ja) * 2013-06-07 2017-09-06 サンデンホールディングス株式会社 往復動式圧縮機
JP6135573B2 (ja) * 2014-03-27 2017-05-31 株式会社豊田自動織機 容量可変型斜板式圧縮機
WO2016113785A1 (ja) * 2015-01-15 2016-07-21 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置及びそれに用いられる圧縮機
CN110821778B (zh) * 2018-08-10 2021-05-07 株式会社丰田自动织机 活塞式压缩机
JP7185568B2 (ja) * 2019-03-20 2022-12-07 サンデン株式会社 可変容量圧縮機
CN114233629A (zh) * 2021-12-08 2022-03-25 好米动力设备有限公司 一种基于磁性液体体积磁致伸缩的压缩机

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DE112011104374T5 (de) 2013-09-12
US20130259714A1 (en) 2013-10-03
CN103261687A (zh) 2013-08-21
DE112011104374B4 (de) 2017-02-02
JP2012127233A (ja) 2012-07-05
CN103261687B (zh) 2015-11-25
JP5697022B2 (ja) 2015-04-08

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