WO2015033391A1 - Compresseur - Google Patents

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Publication number
WO2015033391A1
WO2015033391A1 PCT/JP2013/073715 JP2013073715W WO2015033391A1 WO 2015033391 A1 WO2015033391 A1 WO 2015033391A1 JP 2013073715 W JP2013073715 W JP 2013073715W WO 2015033391 A1 WO2015033391 A1 WO 2015033391A1
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WO
WIPO (PCT)
Prior art keywords
suction
pressure
suction chamber
throttle valve
chamber
Prior art date
Application number
PCT/JP2013/073715
Other languages
English (en)
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 CN201380079294.5A priority Critical patent/CN105579704B/zh
Priority to PCT/JP2013/073715 priority patent/WO2015033391A1/fr
Priority to US14/915,781 priority patent/US20160195077A1/en
Priority to DE112013007398.6T priority patent/DE112013007398B4/de
Publication of WO2015033391A1 publication Critical patent/WO2015033391A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • 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
    • F04B27/1045—Cylinders
    • 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
    • F04B27/12—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 having plural sets of cylinders or pistons
    • 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
    • F04B49/22—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 means of valves
    • F04B49/225—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 means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves

Definitions

  • the present invention relates to a compressor provided with a suction throttle valve that changes the opening of the suction passage in accordance with the difference between the pressure of the suction chamber and the pressure of the suction passage.
  • Patent Document 1 discloses a suction throttle valve that changes the opening degree of the refrigerant circuit from the evaporator outlet to the compressor suction chamber in accordance with the increase or decrease of the refrigerant flow rate.
  • the suction throttle valve described above when the flow rate of the refrigerant is low, the suction pressure pulsation caused by the self-excited vibration of the compressor suction valve propagates to the evaporator through the refrigerant circuit from the evaporator outlet to the compressor suction chamber. Is prevented by reducing the opening of the refrigerant circuit from the evaporator outlet to the compressor suction chamber.
  • the suction throttle valve operates according to the pressure difference between the pressure on the suction passage side (upstream pressure, primary pressure) and the pressure on the suction chamber side (downstream pressure, secondary pressure). Since the body is urged in the valve closing direction by an elastic member (spring), the suction throttle valve causes a pressure loss, and the pressure loss is a factor in the performance deterioration of the refrigerant circuit.
  • a large pressure distribution is generated in the suction chamber, and the region in the suction chamber near the suction throttle valve is a connection region with the suction passage, so that the region in the other suction chambers is larger than the region in the other suction chambers. Since the pressure is in a high region, the valve body of the conventional suction throttle valve operates under the highest pressure in the suction chamber, which has been a factor in increasing pressure loss.
  • an object of the present invention is to provide a compressor that can reduce pressure loss due to a suction throttle valve.
  • a compressor according to the present invention includes a suction chamber formed annularly around a drive shaft, a suction passage communicating with the suction chamber, a pressure of the suction chamber, and the suction passage.
  • a suction throttle valve that changes an opening degree of the suction passage in accordance with a pressure difference between the suction throttle valve and the suction throttle valve having a pressure separated from a region of the suction chamber in the vicinity of the suction throttle valve. The lower pressure in the other area of the suction chamber was introduced through the pressure introduction passage.
  • the pressure in the suction chamber that acts on the valve closing side with respect to the suction throttle valve is introduced as a pressure lower than that in the vicinity of the suction throttle valve. Loss can be reduced.
  • FIG. 2 is an enlarged view of a portion of a suction throttle valve in FIG. 1. It is a figure which shows the structure of the cylinder head shown in FIG. It is sectional drawing which shows the structure of the suction throttle valve in embodiment of this invention. It is a figure which shows the pressure introduction channel
  • variable capacity compressor 100 as an example of a compressor.
  • the variable capacity compressor 100 is provided with a cylinder block 101 having a plurality of cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101, and a valve plate 103 at the other end of the cylinder block 101.
  • a cylinder head 104 A cylinder head 104.
  • the drive shaft 110 is provided across the crank chamber 140 formed by the cylinder block 101 and the front housing 102.
  • a swash plate 111 is disposed around an intermediate portion of the drive shaft 110 in the axial direction.
  • the swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120 so that an inclination angle with respect to 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 rotating relative to the first arm 112 a via the first connecting pin 122.
  • a link arm 121 that is movably coupled and has the other end pivotally coupled to the second arm 111a via a second coupling 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 the range of the maximum tilt angle ( ⁇ max) and the minimum tilt angle ( ⁇ min), and the through hole 111b has a minimum tilt angle restricting portion that contacts the drive shaft 110. Is formed.
  • the minimum inclination restricting portion of the through hole 111b is formed so that the swash plate 111 can be inclined to approximately 0 deg. Yes.
  • an inclination-decreasing spring 114 that biases the swash plate 111 toward the minimum inclination angle is mounted, and between the swash plate 111 and the spring support member 116 provided on the drive shaft 110. Is attached with an inclination increasing spring 115 that urges the swash plate 111 in an increasing direction.
  • the biasing force of the tilt-increasing spring 115 at the minimum tilt angle is set larger than the biasing force of the tilt-decreasing spring 114, and when the drive shaft 110 is not rotating, the swash plate 111 is The biasing force and the biasing force of the tilt angle increasing spring 115 are positioned at an inclination angle that balances.
  • One end of the drive shaft 110 extends through the inside of 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 to block the inside of the crank chamber 140 from the external space.
  • the drive shaft 110 and the rotor 112 are supported by bearings 131 and 132 in the radial direction, and supported by a bearing 133 and a thrust plate 134 in the thrust direction.
  • the gap between the thrust plate 134 of the drive shaft 110 and the thrust plate 134 is adjusted to a predetermined gap by the adjustment screw 135.
  • the power from the external drive source is transmitted to the power transmission device, and the drive shaft 110 rotates in synchronization with the power transmission device.
  • 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 137. Via the piston 136. Accordingly, the piston 136 reciprocates in the cylinder bore 101a by the rotation of the swash plate 111.
  • the cylinder head 104 includes a discharge chamber 142 defined by an annular partition wall 104a at the center, and a suction chamber 141 defined by the partition wall 104a and the outer peripheral wall 104b and surrounding the discharge chamber 142 in an annular shape. It is formed.
  • the suction chamber 141 communicates with the cylinder bore 101a via a suction hole 103a and a suction valve (not shown) provided in the valve plate 103, and the discharge chamber 142 includes a discharge hole 103b and a discharge valve provided in the valve plate 103. It communicates with the cylinder bore 101a via (not shown).
  • the front housing 102, center gasket (not shown), cylinder block 101, cylinder gasket (not shown), valve plate 103, head gasket (not shown), cylinder head 104, and the like are fastened by a plurality of through bolts 105. And a compressor housing is formed.
  • the cylinder head 104 is formed with a suction passage 104c that connects the low-pressure side refrigerant circuit of the refrigeration apparatus (for example, a vehicle air conditioner system) and the suction chamber 141, whereby the suction chamber 141 is connected to the low-pressure side refrigerant circuit of the refrigeration apparatus. Connected.
  • the suction passage 104c extends along the radial direction of the drive shaft 110 from the outside of the cylinder head 104 (drive shaft 110) toward the suction chamber 141.
  • the suction passage 104c includes a suction port 104c1 to which the low-pressure side refrigerant circuit is connected, and a communication hole 104c2 that connects the suction port 104c1 and the suction chamber 141.
  • the suction throttle valve 200 is provided between the communication hole 104c2 and the suction chamber 141. Is arranged.
  • the suction throttle valve 200 operates according to the pressure difference between the suction passage 104c (upstream side) and the suction chamber 141 (downstream side).
  • the suction throttle valve 200 When the pressure difference is equal to or less than a predetermined value, that is, when the refrigerant flow rate is small, the suction throttle valve 200 When the opening area (opening) is reduced to the minimum, the refrigerant flow rate increases and the pressure difference increases beyond a predetermined value, the opening area (opening) of the suction passage 104c is increased.
  • the suction throttle valve 200 restricts the pressure pulsation in the suction chamber 141 from propagating to the evaporator via the low-pressure side refrigerant circuit by restricting the suction passage 104c in the region where the refrigerant flow rate is small.
  • the discharge chamber 142 is connected to the discharge-side external refrigerant circuit of the refrigeration apparatus via the discharge passage 104d.
  • the discharge passage 104 d extends from the outer side of the cylinder head 104 toward the inner side in the radial direction of the drive shaft 110, and communicates with the discharge chamber 142 across the suction chamber 141.
  • the cylinder head 104 is further provided with a control valve 300.
  • the control valve 300 controls the amount of discharge gas introduced into the crank chamber 140 by adjusting the opening of the communication passage 145 that communicates the discharge chamber 142 and the crank chamber 140.
  • the refrigerant in the crank chamber 140 flows to the suction chamber 141 through the communication passage 101b formed by the communication passage 101b, the space 101c, and the orifice 103c formed in the valve plate 103.
  • the discharge capacity of the variable capacity compressor 100 can be variably controlled by changing the pressure of the crank chamber 140 by the control valve 300 and changing the inclination angle of the swash plate 111, that is, the stroke of the piston 136. It has become.
  • the energization amount of the solenoid built in the control valve 300 is adjusted according to the external signal and introduced into the control valve 300 via the communication path 104e.
  • the discharge capacity is variably controlled so that the pressure in the suction chamber 141 becomes a predetermined value.
  • the suction throttle valve 200 includes a cylindrical first housing 201, a bottomed cylindrical second housing 204, a bottomed cylindrical valve body 202, and a compression coil spring 203.
  • the second housing 204 has a cylindrical space 204a for accommodating the valve body 202 and the compression coil spring 203, and a plurality of substantially pentagonal outlet holes 204b having apex angles toward the valve seat 201b are formed on the cylindrical surface.
  • the one end side 204c is fitted and fixed to the outer periphery of the inlet hole 201a of the first housing 201.
  • the valve body 202 is accommodated in the second housing 204 so as to be movable in the axial direction in the space 204 a, and between the bottom side of the internal space of the valve body 202 and the bottom side of the second housing 204, a compression coil spring 203 is provided.
  • the compression coil spring 203 urges the valve body 202 toward the valve seat 201b, that is, toward the valve closing direction.
  • An annular concave portion is formed on the inner peripheral surface of the one end side 204c of the second housing, and an annular convex portion is formed on the outer peripheral surface of the first housing 201 corresponding thereto.
  • Two housings 204 are fixed to the first housing 201.
  • the first housing 201, the second housing 204, and the valve body 202 are resin molded products.
  • annular convex portion is formed on the outer peripheral surface of the flange 201c of the first housing 201 forming one end side of the suction throttle valve 200, and this is fitted to the annular concave portion formed in the communication hole 104c2 of the suction passage 104c.
  • the suction throttle valve 200 is positioned and fixed in the suction passage 104c.
  • the suction throttle valve 200 is disposed in an extended region of the suction passage 104c so that the outlet hole 204b faces the suction chamber 141.
  • the valve body 202 has an end surface 202a that contacts the valve seat 201b and a cylindrical outer peripheral surface 202b.
  • the valve body 202 is slidably supported on the cylindrical inner peripheral surface of the second housing 204, and the cylindrical space 204a passes through the suction passage.
  • the first space 204a1 and the second space 204a2 are defined so as to communicate the 104c and the suction chamber 141. Then, when the valve body 202 moves in the second housing 204 in the axial direction, the opening area of the outlet hole 204b, that is, the opening area (opening) of the suction passage 104c changes.
  • a groove 201d having a predetermined width is formed in a part of the valve seat 201b of the first housing 201, and the apex angle portion of the outlet hole 204b communicates with the internal space of the groove 201d.
  • the suction passage 104c is not completely blocked, and the suction passage 104c passes through the apex corners of the inlet hole 201a, the groove 201d, and the outlet hole 204b.
  • the opening area of the apex corner portion of the outlet hole 204b is smaller than the channel area of the groove 201d, and the opening area of the apex corner portion of the outlet hole 204b at this time Is the minimum opening area (minimum opening).
  • the minimum opening area is set as an area that can prevent the self-excited vibration of the valve body 202 in a region where the refrigerant flow rate is very small, but considering the evacuation inside the variable capacity compressor 100 before filling the refrigerant. , At least larger than the opening area of the orifice 103c.
  • a communication hole 204 d is formed in the bottom wall of the second housing 204, and the communication hole 204 d communicates the second space 204 a 2 defined by the second housing 204 and the valve body 202 and the suction chamber 141.
  • the bottom portion of the second housing 204 of the suction throttle valve 200 accommodates a partition wall 104a that defines the discharge chamber 142 and the suction chamber 141 in the extension region of the suction passage 104c in a recess 104f that is recessed in the discharge chamber 142 side. Is done.
  • the inside of the recess 104f is connected to a suction chamber 141 opposite to the region of the suction chamber 141 where the suction throttle valve 200 is provided via a pressure introduction passage 104g formed across the discharge chamber 142. (Region A in FIG. 3).
  • the pressure introduction passage 104g is linearly formed along the extended region of the suction passage 104c, that is, the radial direction of the drive shaft 110, and the opening end on the bottom wall side of the recess 104f is disposed so as to face the communication hole 204d. Yes.
  • the cross-sectional area of the clearance 150 between the outer peripheral surface of the second housing 204 and the inner peripheral surface of the recess 104f is set to be smaller than the minimum cross-sectional area of the communication hole 104g, and the clearance 150 is the communication hole in the recess 104f.
  • a connection region between 204d and the pressure introduction passage 104g and a region in the suction chamber 141 in the vicinity of the outlet hole 204b of the suction throttle valve 200 (region B in FIG. 3) are defined.
  • the pressure in the region A of the suction chamber 141 facing the shaft center of the drive shaft 110 acts on the second space 204a2 via the pressure introduction passage 104g, the recess 104f, and the communication hole 204d.
  • a seal member such as an O-ring can be disposed in the gap 150.
  • the pressure of the suction passage 104c is introduced to the upstream side of the valve body 202, the pressure of the region A of the suction chamber 141 is introduced to the downstream side of the valve body 202, and the pressure difference between them. That is, the opening degree of the suction passage 104c is adjusted following the change in the refrigerant circulation amount.
  • the pressure difference at which the valve body 202 operates is determined by the pressure receiving area of the valve body 202 and the urging force of the compression coil spring 203.
  • the valve body 202 has a small pressure difference of about 100 kPa.
  • the pressure receiving area and the urging force of the compression coil spring 203 are set.
  • the suction throttle follows the refrigerant circulation amount.
  • the valve 200 adjusts the opening degree of the suction passage 104c.
  • the opening amount of the suction passage 104c increases.
  • the opening amount of the suction passage 104c decreases.
  • the refrigeration apparatus is an air conditioner system for a vehicle
  • the refrigerant circulation amount increases under a so-called high load condition where the vehicle has a large heat load
  • the suction chamber 141 is formed in an annular shape
  • the pressure distribution in the suction chamber 141 is increased.
  • the region in the suction chamber 141 in the vicinity of the suction throttle valve 200 region B in FIG. 3
  • the region is located upstream of the regions in the other suction chambers 141.
  • 141 is the highest pressure region.
  • the pressure in the suction chamber 141 acting on the valve body 202 of the suction throttle valve 200 is the pressure in the region A, and the region A is located on the downstream side away from the region B where the pressure is highest, and is higher than the region B. Pressure is lowered. Accordingly, the suction throttle valve 200 in which the pressure in the region A of the suction chamber 141 acts on the valve body 202 is different from the front and rear differential pressure of the valve body 202 in comparison with the suction throttle valve in which the pressure in the region B of the suction chamber 141 acts on the valve body. Becomes larger and the opening degree becomes larger. As a result, the pressure loss at the suction throttle valve 200 is reduced, and performance degradation due to the provision of the suction throttle valve 200 can be suppressed.
  • a pressure introduction passage 104 g is connected to a region A that faces the region B of the suction chamber 141 where the suction throttle valve 200 is provided across the axis of the drive shaft 110.
  • the pressure in the region A is introduced as the pressure in the suction chamber 141, but the region where the pressure introduction passage 104g is connected is not limited to the region A, and the region of the suction chamber 141 in which the suction throttle valve 200 is provided.
  • the region can be a region having a lower pressure than the region B, away from the region B.
  • the region of the suction chamber 141 where the pressure introduction passage 104g opens is a region where the pressure is lower than the pressure in the region B by a predetermined pressure (for example, 100 kPa) under a high load condition, and in particular, the highest pressure in the suction chamber 141.
  • a predetermined pressure for example, 100 kPa
  • the pressure introduction passage 104g is not limited to a structure that is linearly formed in the radial direction of the drive shaft 110, and may have a structure including a bent portion in the middle.
  • the pressure introduction passage 104g is projected in the axial direction of the drive shaft 110 as described above.
  • the pressure in the vicinity of the region B facing the region B of the suction chamber 141 where the suction throttle valve 200 is provided that is, the pressure in the region A farthest from the region B is set. Since it becomes the lowest, the pressure introduction passage 104g is connected to the region A in the example shown in FIG.
  • the opening degree under a high load condition is larger than that of the intake throttle valve that operates based on the pressure in the region B, and the effect of reducing the pressure pulsation tends to decrease.
  • the pressure pulsation level in the suction chamber 141 that manifests as noise in the passenger compartment under a high load condition is small, and this is not substantially a problem.
  • the pressure distribution (pressure variation) in the suction chamber 141 is reduced, so that the pressure in the region A approaches the pressure in the region B, and the suction throttle valve The opening degree of 200 approaches when operating according to the pressure in region B. Since the pressure pulsation level in the suction chamber 141 tends to increase under low load conditions where the refrigerant circulation rate decreases, the pressure pulsation level operates according to the pressure in the region B under low load conditions where the effect of reducing pressure pulsation is required. The effect of reducing the pressure pulsation is almost the same as that of the case.
  • the suction throttle valve 200 is configured such that when a pressure distribution is generated in the suction chamber 141, the pressure in a region where the pressure is low acts on the valve body 202. Under a high heat load condition where the pressure increases, the performance degradation due to the intake throttle valve 200 can be suppressed without impairing the reduction effect of the vehicle interior noise caused by the suction pressure pulsation.
  • the region where the pressure is lowest in the suction chamber 141 is The suction throttle valve 200 is not the region A facing the region B of the suction chamber 141 where the suction throttle valve 200 is provided, but the region AA shown in FIG. 5, that is, the regions AA and BB sandwiching the narrowed portion of the suction chamber 141.
  • the area AA far from the area B of the nearby suction chamber 141 may be the lowest pressure area in the suction chamber 141.
  • a pressure introduction passage 104g2 extending from the region AA in the radial direction of the cylinder head 104 is formed toward the pressure introduction passage 104g1 formed in the extension region of the suction passage 104c from the region B.
  • the pressure introduction passage 104g1 and the pressure introduction passage 104g2 can be communicated to introduce the pressure in the area AA into the suction throttle valve 200.
  • the pressure introduction passage 104g1 communicating with the communication hole 204d of the second housing 204 extends to the extended region of the suction passage 104c, that is, to the vicinity of the center in the radial direction along the radial direction of the cylinder head 104 (drive shaft 110). Since it is extended, the pressure introduction passage 104g is formed by extending the pressure introduction passage 104g2 in the radial direction from the region regardless of the angular position of the region where the pressure away from the region B is lower. it can.
  • the gap 150 includes a connection region between the communication hole 204 d in the recess 104 f and the pressure introduction passage 104 g, and a region in the suction chamber 141 near the outlet hole 204 b of the suction throttle valve 200 (region in FIG. 3).
  • the region can be defined by an annular gap 160 between the bottom of the second housing 204 and the bottom wall of the recess 104f.
  • a seal member such as an O-ring can be disposed in the annular gap 160.
  • the bottom portion of the second housing 204 and the bottom wall of the recess 104f are brought into contact with each other, and the connection region between the communication hole 204d in the recess 104f and the pressure introduction passage 104g and the suction throttle valve 200 are contacted by the annular contact portion.
  • a region in the suction chamber 141 in the vicinity of the outlet hole 204b (region B in FIG. 3) can be defined.
  • the contact portion also functions as the positioning of the suction throttle valve 200.
  • the structure is not limited to the structure in which the other end side of the suction throttle valve 200 (the bottom wall side of the second housing 204) is accommodated in the recess 104f.
  • a plane corresponding to the bottom wall of the second housing 204 is formed integrally with the partition wall 104 a that partitions the discharge chamber 142 and the suction chamber 141, and a gap between this plane and the bottom wall of the second housing 204 is partitioned. It can be a means.
  • the axis of the suction passage 104c can be set on a plane perpendicular to the axis of the drive shaft 110 from the radially outer side of the cylinder head 104 toward the suction chamber 141, and also a plane orthogonal to the axis of the drive shaft 110.
  • the axis of the suction passage 104c can be inclined.
  • the suction throttle valve 200 may be configured such that when the one end surface 202a of the valve body 202 is seated on the valve seat 201b, the suction passage 104c is not completely blocked, but the suction passage 104c is fully closed.
  • 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 Variable capacity compressor, 101 ... Cylinder block, 102 ... Front housing, 04 ... Cylinder head, 104c ... Suction passage, 104g ... Pressure introduction passage, 110 ... Drive shaft, 141 ... Suction chamber, 142 ... Discharge chamber, 200 ... Suction throttle valve, 201 ... first housing, 204 ... second housing, 202 ... valve, 203 ... compression coil spring

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

Le problème décrit par la présente invention est de réduire une perte de pression d'un compresseur provoquée par un papillon des gaz à aspiration. La solution selon l'invention porte sur un compresseur (100) équipé : d'une chambre d'aspiration (141) qui est de forme annulaire autour d'un arbre d'entraînement (110) ; d'un chemin d'aspiration (104c) qui est relié à la chambre d'aspiration (141) ; et d'un papillon des gaz à aspiration (200) qui modifie le degré d'ouverture du chemin d'aspiration (104c) conformément à une différence de pression entre la pression dans la chambre d'aspiration (141) et la pression dans le chemin d'aspiration (104c). La pression dans une région de la chambre d'aspiration (141), dans laquelle la pression est plus basse, qui est éloignée d'une autre région de la chambre d'aspiration (141) proche du papillon des gaz à aspiration (200), est introduite dans le papillon des gaz à aspiration (200) par le biais d'un chemin d'introduction de pression (104g). Ainsi, la différence entre les pressions avant et après le papillon des gaz à aspiration (200) augmente encore, ce qui permet d'augmenter encore le degré d'ouverture. En conséquence, une perte de pression au niveau du papillon des gaz à aspiration (200) est réduite, et la détérioration des performances due à la présence du papillon des gaz à aspiration (200) peut être supprimée.
PCT/JP2013/073715 2013-09-03 2013-09-03 Compresseur WO2015033391A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201380079294.5A CN105579704B (zh) 2013-09-03 2013-09-03 压缩机
PCT/JP2013/073715 WO2015033391A1 (fr) 2013-09-03 2013-09-03 Compresseur
US14/915,781 US20160195077A1 (en) 2013-09-03 2013-09-03 Compressor
DE112013007398.6T DE112013007398B4 (de) 2013-09-03 2013-09-03 Kompressor mit verringertem Druckabfall im Ansaugdrosselventil

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6456972A (en) * 1987-08-26 1989-03-03 Hitachi Ltd Displacement control valve
JPH0579456A (ja) * 1991-09-18 1993-03-30 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH0735039A (ja) * 1993-07-19 1995-02-03 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH0742669A (ja) * 1993-07-28 1995-02-10 Toyota Autom Loom Works Ltd 往復動型圧縮機
JP2006214396A (ja) * 2005-02-07 2006-08-17 Sanden Corp 開度調整弁
JP2009079519A (ja) * 2007-09-26 2009-04-16 Sanden Corp 圧縮機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07139474A (ja) 1993-11-17 1995-05-30 Toyota Autom Loom Works Ltd 圧縮機の起動負荷低減装置
JPH10281060A (ja) * 1996-12-10 1998-10-20 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP4656044B2 (ja) * 2006-11-10 2011-03-23 株式会社豊田自動織機 圧縮機の吸入絞り弁
JP2009102989A (ja) 2007-10-19 2009-05-14 Sanden Corp 可変容量圧縮機
JP4858409B2 (ja) * 2007-11-05 2012-01-18 株式会社豊田自動織機 可変容量圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6456972A (en) * 1987-08-26 1989-03-03 Hitachi Ltd Displacement control valve
JPH0579456A (ja) * 1991-09-18 1993-03-30 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH0735039A (ja) * 1993-07-19 1995-02-03 Toyota Autom Loom Works Ltd 往復動型圧縮機
JPH0742669A (ja) * 1993-07-28 1995-02-10 Toyota Autom Loom Works Ltd 往復動型圧縮機
JP2006214396A (ja) * 2005-02-07 2006-08-17 Sanden Corp 開度調整弁
JP2009079519A (ja) * 2007-09-26 2009-04-16 Sanden Corp 圧縮機

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DE112013007398T5 (de) 2016-06-02
CN105579704A (zh) 2016-05-11
CN105579704B (zh) 2017-09-29
US20160195077A1 (en) 2016-07-07
DE112013007398B4 (de) 2023-06-22

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