Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
  • F04B2027/1809—Controlled pressure
  • F04B2027/1813—Crankcase pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
  • F04B2027/1822—Valve-controlled fluid connection
  • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
  • F04B2027/184—Valve controlling parameter
  • F04B2027/1854—External parameters
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
  • F04B2027/184—Valve controlling parameter
  • F04B2027/1859—Suction pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
  • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
  • F04B27/14—Control
  • F04B27/16—Control of pumps with stationary cylinders
  • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
  • F04B27/1804—Controlled by crankcase pressure
  • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
  • F04B2027/1881—Suction pressure

Definitions

• the present invention relates to a capacity control valve for a clutchless variable displacement swash plate compressor that is directly connected to a drive source without a clutch.
• Capacity control of a clutchless variable displacement swash plate compressor that opens and closes a valve hole formed in a communication path between a discharge chamber and a crank chamber of a variable displacement swash plate compressor to control the discharge capacity of the compressor
• a valve hole that communicates with the crank chamber at all times, an internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure, and an internal control valve
• the internal control valve is set to an operating state in which the valve body opens and closes the valve hole in response to expansion and contraction of the pressure-sensitive member, and an inoperative state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member.
• Patent Document 1 discloses a capacity control valve that includes an electromagnetic solenoid for switching and controls the discharge capacity so that the suction pressure and the discharge pressure have a predetermined correlation. Patent Document 1 describes that in the region of Pd> Pd, the capacity control characteristic is expressed by the following equation.
• Patent Document 1 Japanese Patent Laid-Open No. 7-127566
• the capacity control valve disclosed in Patent Document 1 has the following problems. Since the discharge pressure Pd biases the valve body in the closing direction, in order to demagnetize the electromagnetic solenoid and force the valve body to open, the force of the opening panel of the electromagnetic solenoid must be (Pd-Pc) S or higher.
• an object of the present invention is to provide a capacity control valve for a clutchless variable capacity swash plate compressor that can be made smaller than the capacity control valve disclosed in Patent Document 1. There is to do.
• a capacity control valve of a clutchless variable displacement swash plate compressor opens and closes a communication path between a discharge chamber and a crank chamber of the variable displacement swash plate compressor.
• An internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of the pressure-sensitive member, and is connected to the internal control valve, and the internal control valve is used to expand and contract the pressure-sensitive member.
• the valve body has an operation switching device that switches between an operation state in which the valve body opens and closes the valve hole and a non-operation state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. It consists of the capacity
• valve hole is always in communication with the discharge chamber, the force by which the discharge pressure Pd urges the valve body in the closing direction is reduced compared to the capacity control valve of Patent Document 1 described above.
• the switching device that forcibly opens the valve disc can be downsized.
• the operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and the electromagnetic solenoid is demagnetized. It is preferable that the internal control valve is configured to be in an inactive state when it is! With this configuration, the variable capacity swash plate compressor can be switched between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid.
• the control device for the variable capacity swash plate compressor is simplified.
• the electromagnetic solenoid positions the internal control valve in the operating position when the electromagnetic solenoid is excited, and the movable iron core connected to the internal control valve. It is preferable to have a positioning member. By arranging the positioning member, it is possible to position the internal control valve to the operating position by exciting the electromagnetic solenoid, and it is possible to switch to the operating state of the variable capacity swash plate compressor by exciting the electromagnetic solenoid. .
• the positioning member is formed by one end of the pressure-sensitive member and an end surface of the case of the electromagnetic solenoid. Positioning member force By forming one end of the pressure-sensitive member and the case of the electromagnetic solenoid, it is not necessary to separately provide a special positioning member, and the structure of the capacity control valve is simplified.
• the electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force.
• the control valve is deactivated. If the electromagnetic solenoid release panel renders the internal control valve inactive, there is no need to separately provide a panel for disabling the internal control valve, and the structure of the capacity control valve is simplified.
• the internal control valve has a pressure-sensitive rod formed in the valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body.
• the cross-sectional area of the pressure-sensitive rod is set larger than the cross-sectional area of the valve hole.
• the internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body.
• the cross-sectional area of the pressure-sensitive rod is set smaller than the cross-sectional area of the valve hole.
• the valve hole is always in communication with the discharge chamber, so that the force by which the discharge pressure urges the valve body in the closing direction is provided.
• the switching device for forcibly opening the valve body can be made smaller than the capacity control valve of Patent Document 1. Therefore, the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention can be reduced in size compared to the capacity control valve of Patent Document 1.
• FIG. 1 is a longitudinal sectional view of a clutchless variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention.
• FIG. 2 is a cross-sectional view of a capacity control valve according to an embodiment of the present invention
• FIGS. 2 (A) and 2 (B) are diagrams showing the operation of the internal control valve when the electromagnetic solenoid is excited
• FIG. 2 (C) is a diagram showing the operation of the internal control valve when the electromagnetic solenoid is demagnetized
• FIG. 2 (D) is an enlarged partial sectional view of the internal control valve.
• FIG. 3 is a control characteristic diagram of a displacement control valve according to an embodiment of the present invention
• FIG. 3 (A) is a control characteristic diagram when Sr> Sv
• FIG. 3 (B) is a control characteristic when Sr> Sv.
• a variable capacity swash plate compressor 1 includes a main shaft 10, a rotor 11 fixed to the main shaft 10, and a swash plate 12 supported on the main shaft 10 so that the tilt angle is variable.
• the swash plate 12 is connected to the rotor 11 via a link mechanism 13 that allows the tilt angle of the swash plate 12 to be changed, and rotates in synchronization with the rotor 11 and the main shaft 10.
• the piston 15 is engaged with the swash plate 12 via a pair of slides 14 that are in sliding contact with the outer peripheral edge of the swash plate 12.
• the piston 15 is inserted into a cylinder bore 16a formed in the cylinder block 16 !.
• a plurality of pistons 15 are arranged around the main shaft 10 at intervals in the circumferential direction.
• a crank chamber 17 that houses the main shaft 10, the rotor 11, and the swash plate 12 is formed by a cylinder block 16 and a dish-shaped front housing 18.
• the main shaft 10 extends through the front housing 18 to the outside.
• a shaft sealing member 19 for sealing the front housing penetrating portion of the main shaft 10 is disposed in the front housing 18.
• a pulley 20 is fixed to the tip of the main shaft 10.
• the pulley 20 is connected to a vehicle engine (not shown) via a belt (not shown), for example.
• a cylinder head 23 that forms a suction chamber 21 and a discharge chamber 22 is disposed at a position opposite to the front housing 18 of the cylinder block 16.
• the suction chamber 21 is connected to an external circuit, for example, an evaporator (not shown) provided in the refrigeration cycle of the vehicle air conditioner via a suction port (not shown).
• the discharge chamber 22 is connected to a discharge port (not shown).
• it is connected to an external circuit, for example, a condenser (not shown) provided in the refrigeration cycle of the vehicle air conditioner.
• a valve plate 24 is formed between the cylinder block 16 and the cylinder head 23.
• the valve plate 24 has a suction port 2la communicating with the cylinder bore 16a and a discharge port 22a.
• a discharge valve and a suction valve are mounted on the valve plate 24 (not shown).
• the crank chamber 17 and the suction chamber 21 communicate with each other through an orifice hole 24 a formed in the valve plate 24.
• the front housing 18, the cylinder block 16, the valve plate 24, and the cylinder head 23 are integrated by a plurality of through bolts 25 that are spaced apart from each other along a circumference centered on the main shaft 10. It is concluded.
• a capacity control valve 2 for controlling the discharge capacity of the variable capacity swash plate compressor 1 is fitted and fixed in a recess 26 formed in the cylinder head 23 adjacent to the discharge chamber 22. As shown in FIGS. 1 and 2, the capacity control valve 2 includes an internal control valve 100 and an electromagnetic solenoid 120.
• the internal control valve 100 has a cylindrical valve housing 101.
• Two O-rings 101a and 101b closely fitted to the outer peripheral surface of the valve housing 101 and one O-ring 121a tightly fitted to the outer peripheral surface of the case 121 of the electromagnetic solenoid 120
• the valve housing 101 is formed with a transverse partition wall 104 that divides the internal space of the valve housing 101 into a pressure-sensitive chamber 102 on one end side and a valve chamber 103 on the other end side.
• the transverse partition wall 104 is formed with a rod through hole 105 communicating with the pressure sensing chamber 102 and a valve hole 106 communicating with the valve chamber 103.
• the rod through hole 105 and the valve hole 106 are arranged coaxially and communicate with each other.
• a communication hole 107 is formed in the horizontal partition wall 104 so as to pass through the horizontal partition wall 104 in the radial direction through a communication portion between the rod through hole 105 and the valve hole 106.
• the pressure sensing chamber 102 communicates with the suction chamber 21 via a communication hole 108 formed in the peripheral wall of the valve housing 101, a closed space 27c, and a communication passage 23a formed in the cylinder head 23. ing .
• the communication hole 107 communicates with the discharge chamber 22 via a closed space 27b and a communication passage 23b formed in the cylinder head 23.
• the valve hole 106 communicating with the communication hole 107 is always in communication with the discharge chamber 22.
• the valve chamber 103 communicates with the crank chamber 17 through a closed space 27a, a communication path 23c formed in the cylinder head 23, and a communication path 16b formed in the cylinder block 16. ing.
• a base assembly 109 functioning as a pressure sensing device in which the inside is evacuated and the panel is arranged is disposed.
• One end of the pressure sensitive rod 110 is connected to one end 109a of the bellows assembly 109, and the other end is slidably inserted into the rod through hole 105.
• a small-diameter rod 111 extending from the other end of the pressure-sensitive rod 110 is passed through the valve hole 106 so as to be freely movable.
• a valve body 112 connected to the end of the small-diameter rod 111 is disposed in the valve chamber 103.
• a panel 113 that urges the valve body 112 toward the valve hole 106 is disposed in the valve chamber 103.
• the internal control valve 100 is formed by a series of structures from the valve housing 101 to the panel 113.
• the end of the valve housing 101 of the internal control valve 100 on the pressure sensing chamber 102 side is press-fitted and fixed to one end of the case 121 of the electromagnetic solenoid 120.
• the O-ring 121a that forms the closed space 27c is fitted to the outer peripheral surface on one end side of the case 121.
• the electromagnetic solenoid 120 includes a fixed iron core 122 disposed in the case 121, a movable iron core 123 disposed with one end facing the one end of the fixed iron core 122, and the movable iron core 123 from the fixed iron core. It has an open panel 124 that urges in a separating direction, and an electromagnetic coil 125 that surrounds the fixed iron core 122 and the movable iron core 123.
• the space for accommodating the movable iron core 123 communicates with the pressure sensing chamber 102 and is at the same pressure as the pressure sensing chamber 102.
• the other end 109b of the bellows assembly 109 is connected to the other end of the movable iron core 123.
• the other end 109b is disposed so as to be engageable with the end surface inner edge portion 121a in the vicinity of the one end of the case 121 of the electromagnetic solenoid 120.
• the electromagnetic coil 125 is excited to attach the open panel 124 as shown in FIGS. 2 (A) and 2 (B).
• the movable iron core 123 toward the fixed iron core 122 against the force, and bring the other end 10 9b of the bellows assembly 109 into contact with the inner edge 12 lb of the end face 121 of the electromagnetic solenoid 120.
• the internal control valve 100 enters an operation state in which the valve body 112 opens and closes the valve hole 106 in response to expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.
• the bellows assembly 109 contracts and is connected to the bellows assembly 109 via the pressure-sensitive rod 110 and the small-diameter rod 111, as shown in FIG.
• the valve hole 106 is closed. Thereby, the supply of the high-pressure refrigerant gas from the discharge chamber 22 to the crank chamber 17 is stopped.
• the orifice passage 24a has a sufficient cross-sectional area to discharge blow-by gas leaking from the cylinder bore 16a to the crank chamber 17 to the suction chamber 21 when the piston 15 compresses the refrigerant gas in the cylinder bore 16a.
• the crank chamber pressure gradually decreases.
• the swash plate inclination angle increases, the discharge capacity of the variable displacement swash plate compressor 1 increases!], And the suction pressure gradually decreases.
• the opening and closing of the valve hole 106 is repeated so that the suction pressure becomes a set value, and the discharge capacity of the variable capacity swash plate compressor 1 is variably controlled.
• the other end 109b of the bellows assembly 109 receives the biasing force of the open panel 124 and the inner edge 121b of the end surface of the case 121 of the electromagnetic solenoid 120 as shown in FIG. ,
• the bellows assembly 109 is positioned in the inoperative position and the internal control valve 100 is positioned in the inoperative position.
• the internal control valve 100 is in an inoperative state in which the valve body 112 opens the valve hole 106 regardless of the expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.
• the lift amount of the valve body 112 is regulated by the end 109 a of the bellows assembly 109 coming into contact with the horizontal partition wall 104.
• variable capacity swash plate compressor 1 In this state, high-pressure refrigerant gas is supplied from the discharge chamber 22 to the crank chamber 17, the crank chamber pressure increases, the swash plate inclination decreases to the minimum inclination, and the discharge capacity of the variable capacity swash plate compressor 1 increases. Reduced to minimum capacity and maintained at minimum capacity. Since the discharge capacity of the variable capacity swash plate compressor 1 can be minimized by demagnetizing the electromagnetic coil 125, the capacity control valve 2 is connected to an external drive source without a clutch. Can be used as a variable capacity swash plate compressor.
• the discharge pressure Pd acts on the valve body 112 and the pressure-sensitive rod 110, so the force that the discharge pressure Pd urges in the direction to close the valve body 112 is (Sr ⁇ Sv) Pd. Since (Sr ⁇ Sv) is very small, (Sr ⁇ Sv) Pd is much smaller than PdSv in Patent Document 1 described above. Therefore, the capacity control valve 2 can be reduced in size compared to the capacity control valve of Patent Document 1.
• the slope of the correlation line of Ps with respect to Pd is-(Sr-Sv) Z ⁇ Sb- (Sr-Sv) ⁇ , so if the cross-sectional area Sr of the pressure-sensitive rod is changed, The inclination can be changed without changing the cross sectional area Sv of the valve hole and the effective cross sectional area Sb of the bellows assembly, which are the basic specifications of the capacity control valve 2. Therefore, the capacity control characteristic can be easily changed.
• the slope of the correlation line of Ps with respect to Pd is — (Sr—Sv) Z ⁇ Sb— (Sr—Sv) ⁇ , so the cross sectional area Sv of the valve hole 106 must be changed.
• the bellows effective cross-sectional area Sb can be reduced without changing the slope of the correlation line of Ps with respect to Pd. Therefore, downsizing is easy.
• the capacity control valve 2 can switch the clutchless variable capacity swash plate compressor 1 between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid 120. If used, the control device of the variable capacity swash plate compressor 1 is simplified.
• the positioning member constituted by the other end 109b of the bellows assembly 109 and the end surface inner edge 121b of the case 121 of the electromagnetic solenoid 120 is disposed, Positioning of the internal control valve 100 to the operating position by excitation is possible, and switching to the capacity control state of the variable displacement swash plate compressor 1 by excitation of the electromagnetic solenoid 120 is possible.
• the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge 121b of the end surface 121 of the case 121 of the electromagnetic solenoid 120, so there is no need to separately provide a special positioning member.
• the valve structure has been simplified.
• variable capacity swash plate compressor 1 discharge capacity is reduced.
• variable capacity swash plate compressor 1 is operated with an excessive load, and the occurrence of damage is suppressed.
• the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge portion 12 lb of the end surface 121 of the electromagnetic solenoid 120.
• the adsorbing portion of the movable iron core 123 and the fixed iron core 122 A positioning member may be formed.
• an adjustment member that adjusts the urging force of the panel 113 from the outside may be provided.
• the present invention can be widely used for a capacity control valve of a clutchless variable capacity swash plate compressor.
• it is suitable as a capacity control valve for a compressor provided in a refrigeration cycle of a vehicle air conditioner.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
• Control Of Positive-Displacement Pumps (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=35783900

Family Applications (1)

Country Status (6)

Cited By (1)

Families Citing this family (7)

Citations (5)

Family Cites Families (11)

• 2004
  • 2004-07-13 JP JP2004206550A patent/JP2006029150A/ja active Pending
• 2005
  • 2005-07-11 WO PCT/JP2005/012760 patent/WO2006006560A1/ja not_active Application Discontinuation
  • 2005-07-11 EP EP05758283A patent/EP1775470B1/en not_active Expired - Fee Related
  • 2005-07-11 US US11/571,884 patent/US20070183904A1/en not_active Abandoned
  • 2005-07-11 CN CNB2005800234342A patent/CN100507267C/zh not_active Expired - Fee Related
  • 2005-07-11 DE DE602005013969T patent/DE602005013969D1/de active Active

Patent Citations (5)

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