Patent Application
20050163624
The present invention relates to a variable displacement compressor used in an air conditioning system for vehicles, etc., and specifically to a variable displacement compressor capable of allowing a smooth operation of a displacement control valve at a high reliability and capable of simplifying the processing of the compressor as a whole.
As a variable displacement compressor provided in a refrigeration circuit of an air conditioning system for vehicles, etc., a compressor such as one disclosed in JP-A-11-107929 is known. To this variable displacement compressor, in order to control its displacement for discharge, a displacement control valve is provided, in which a control point for a pressure in a suction chamber is decided to be one-to-one relative to an amount of electricity applied to an electromagnetic actuator, and which can maintain the variable displacement compressor forcibly at a minimum displacement condition when it is not excited.
This displacement control valve is structured as depicted in
Further, a surface 118b of valve element 118 opposite to a contact surface 118a being brought into contact with the valve seat is formed so as to receive a pressure in a crank chamber through a pressure guiding passage 122. A pressure receiving area for a pressure in a crank chamber of contact surface 118a side of valve element 118 and a pressure receiving area for a pressure in a crank chamber of surface 118b opposite thereto are set at almost the same area. Further, a side surface 118c of valve element 118 is supported movably by valve casing 111, a gap between the side surface 118c and the inner circumferential surface of valve casing 111 is set very small, and in this portion, valve element 118 is substantially slid in its axial direction.
In the above-described mechanism of the displacement control valve of the variable displacement compressor, although a pressure in a crank chamber is controlled by moving and controlling valve element in its axial direction, thereby controlling the displacement for discharge, totally four sliding parts between transmission rod 116 and valve casing 111, between side surface 118c of valve element 118 and valve casing 111, between transmission rod 120 and fixed iron core 121a and between plunger 119 and housing 110 are present in this mechanism for movement and control in the axial direction of valve element 118. Therefore, when valve element 118 is moved and controlled in its axial direction, because there occur sliding resistances in the respective sliding parts, if these sliding resistances are great, there is a fear to deteriorate the movement of valve element 118. Moreover, because four sliding parts are arranged in the same axial direction, it may be difficult to maintain the respective sliding parts accurately at respective predetermined positional relationships without shifting, and also from this point of view, there is a fear to enlarge the sliding resistance. If the movement of valve element 118 is deteriorated by such a sliding resistance, a smooth control of displacement for discharge of the variable displacement compressor may be damaged.
Accordingly, an object of the present invention is to provide a variable displacement compressor which can reduce a sliding resistance accompanying with the movement of a valve element of a displacement control valve, thereby controlling displacement for discharge smoothly.
Another object of the present invention is to provide a structure wherein, in addition to the above-described structure for reducing the sliding resistance, it is possible to form a fixed orifice, which has been formed at a cylinder block side or the vicinity thereof and provided at a position in a pressure relief passageway communicating from a crank chamber to a suction chamber, in a displacement control valve, thereby simplifying the processing, in particular, simplifying the processing of the cylinder block side.
To achieve the above objects, a variable displacement compressor according to the present invention has a discharge chamber, a suction chamber and a crank chamber, the compressor comprises a displacement control valve disposed at a position in a discharge pressure supply passageway capable of communicating with the crank chamber from the discharge chamber, and a fixed orifice provided at a position in a pressure relief passageway communicating with the suction chamber from the crank chamber, the displacement control valve is controlled in opening/closing operation to regulate a pressure in the crank chamber to control a piston stroke, wherein the displacement control valve further comprises a pressure sensing member being expanded and contracted by sensing a pressure in the suction chamber or the crank chamber, a valve element one end of which is brought into contact with the pressure sensing member and which has a valve part opening and closing a valve hole formed in the discharge pressure supply passageway in response to an expansion/contraction of the pressure sensing member, a valve chamber in which the valve part is disposed and to which a pressure in the crank chamber acts, a partition wall disposed around the valve element at a position in an axial direction of the valve element, a pressure chamber which is partitioned from the valve chamber by the partition wall and to which a pressure in the suction chamber acts, and a solenoid provided to the other end of the valve element and capable of controlling an opening degree of the valve part by increase/decrease of an electromagnetic force, and a flow passage from the valve chamber to the pressure chamber is formed in a portion disposed with the partition wall, whereby a gap is defined for forming a non-contact structure which does not give a sliding resistance relative to a movement of the valve element in its axial direction.
Namely, in this structure, a conventional sliding part having been present in the portion of the partition wall is abolished, and a gap with a non-contact structure is formed and this gap is positively utilized as a flow passage from the valve chamber to the pressure chamber. By this structure, the number of the conventional four sliding parts as aforementioned can be surely reduced by at least one.
In this variable displacement compressor, the above-described gap may be formed as the fixed orifice, and by this, the fixed orifice may be formed in the displacement control valve and it is not necessary to form it at another portion.
Further, the above-described partition wall may be fixed at a valve casing side of the displacement control valve, and the above-described gap may be defined between an inner circumferential surface of the partition wall and an outer circumferential surface of the valve element. Alternatively, the partition wall may be fixed to the valve element, and the gap may be defined between an outer circumferential surface of the partition wall and an inner circumferential surface of a valve casing of the displacement control valve.
Moreover, it is preferred to employ a structure wherein the solenoid comprises an electromagnetic coil excited for generating an electromagnetic force, a fixed iron core for generating a magnetic force by excitation of the electromagnetic coil, and a plunger attracted and moved to fixed iron core side by the magnetic force of the fixed iron core, and in this structure, the other end of the valve element is fixed to the plunger, the plunger is held slidably in an axial direction of the valve element, and a gap is defined between the fixed iron core and the valve element for forming a non-contact structure which does not give a sliding resistance relative to a movement of the valve element in its axial direction. By this, the sliding parts present in the respective portions of the fixed iron core and the plunger in the aforementioned conventional structure may become only a sliding part of the plunger. Therefore, in this structure, the number of the conventional four sliding parts becomes totally two, namely, the sliding parts in the axially extending portion of the valve element including the plunger become only two sliding parts at both end portions (two-point suspension), and even from the viewpoint of the principle of supporting mechanism, a smooth operation of the movement of the valve element may be assured.
Thus, in the variable displacement compressor according to the present invention, since a non-contact gap structure is formed at a portion of the partition wall and generation of a sliding resistance is prevented at this portion, and the number of sliding parts may be reduced also in the solenoid side, the sliding resistance accompanying with the movement of the valve element may be greatly reduced, and a stable and smooth control of displacement for discharge may be achieved by the smooth operation of the valve element.
Further, because the gap in the partition wall may be formed as the fixed orifice, it becomes unnecessary to provide the fixed orifice at another portion of the compressor, thereby simplifying the processing of the cylinder block and its vicinity portion and reducing the cost as a whole.
Hereinafter, desirable embodiments of the present invention will be explained referring to figures.
In
One end of compressor main shaft 56 extends to an outside through a boss 52a protruded toward an outside of front housing 52, and an electromagnetic clutch 70 is provided around the boss 52a via a bearing 60. Electromagnetic clutch 70 comprises a rotor 71 provided around boss 52a, a magnet unit 72 contained in the rotor 71, and a clutch plate 73 provided on one outer end surface of the rotor 71. One end of compressor main shaft 56 is connected to clutch plate 73 via a fastener 74 such as a bolt. A seal member 52b is inserted between compressor main shaft 56 and boss 52a, thereby isolating between the inside and the outside. Further, the other end of compressor main shaft 56 is present in cylinder block 51, and it is supported by a supporting member 78. Where, labels 75, 76 and 77 indicate bearings, respectively.
A piston 62 is inserted free to be slid into cylinder bore 51a. The periphery of inclined plate 57 is disposed in a recessed portion 62a formed at the inside of one end of piston 62, and by forming a structure for engaging piston 62 and inclined plate 57 to each other via a pair of shoes 63, the rotational movement of inclined plate 57 is transformed into the reciprocating movement of piston 62.
A suction chamber 65 and a discharge chamber 64 are formed in rear housing 53 separately from each other. Suction chamber 65 can communicate with cylinder bore 51a via a suction port 81 provided on valve plate device 54 and a suction valve (not shown), and discharge chamber 64 can communicate with cylinder bore 51a via a discharge port 82 provided on valve plate device 54 and a discharge valve (not shown). Crank chamber 55 communicates with a gas chamber 84 formed at a shaft end extended portion of compressor main shaft 56, through a gap between compressor main shaft 56 and bearing 77.
A displacement control valve 1 is provided in a recessed portion of a rear wall of rear housing 53 in this variable displacement compressor 50. This displacement control valve 1 is used for controlling a displacement for discharge (displacement for compression, that is, a stroke of piston 62). Displacement control valve 1 is provided at a portion in the discharge pressure supply passageway capable of communicating from discharge chamber 64 to crank chamber 55, and a part of this discharge pressure supply passageway is formed from a communication passage 66 to gas chamber 84 and a communication passage 68 to discharge chamber 64. Further, a pressure relief passageway communicating from crank chamber 55 to suction chamber 65 is provided, and a part thereof is formed from a communication passage 67.
As depicted in
A pressure in crank chamber 55 acts in valve chamber 12, a pressure in suction chamber 65 acts to bellows 6, and the pressure in suction chamber 65 acts also in pressure chamber 17 through pressure sensing chamber 3 and communication passage 16. Further, valve part 11 of valve element 9 controls to open and close the discharge pressure supply passageway communicating from discharge chamber 64 to crank chamber 55 (valve chamber 12) on the way of the passageway. Furthermore, gap 14 in partition wall 15 forms a fixed orifice provided on the way of the pressure relief passageway communicating from crank chamber 55 (valve chamber 12) to suction chamber 65 side (pressure chamber 17 side). Where, the discharge pressure acting to transmission rod 10 of valve element 9 acts to almost the same areas of the upper and lower portions in the figure and these pressured acted to those portions are cancelled by each other, and as a result, the discharge pressure almost does not act in the axial direction of valve element 9. Therefore, valve element 9 is controlled in opening/closing operation substantially in response to the electromagnetic force and the pressure in the suction chamber acting to bellows 6.
In the above-described variable displacement compressor 50 having displacement control valve 1, when a predetermined current is applied to electromagnetic coil 22, an electromagnetic force acts to the surfaces facing to each other of plunger 21 and fixed iron core 19, and a force attracting plunger 21 toward fixed iron core 19 (a force in the valve closing direction) acts. When this electromagnetic force becomes higher than a certain level, valve part 11 is closed, and the communication between discharge chamber 64 and crank chamber 55 is interrupted. By this, the gas in discharge chamber 64 is not introduced into crank chamber 55, and a gas flow occurs from crank chamber 55 toward suction chamber 65 through fixed orifice (gap 14). Because this fixed orifice has a diameter necessary and enough to flow a blowby gas, which generates when piston 62 compresses the gas, to suction chamber 65 side, the pressure in crank chamber 55 reduces to become substantially the same pressure as that in suction chamber 65, and the compressor is maintained at a maximum displacement and the pressure in suction chamber 65 is gradually reduced.
When the pressure in suction chamber 65 is reduced down to a predetermined value, because bellows 6 expands and valve element 9 operates in its opening direction, the gas in discharge chamber 64 is introduced into crank chamber 55 side, and the displacement for discharge is decreased by increase of a pressure difference between crank chamber 55 and suction chamber 65. By this, when the pressure in suction chamber 65 increases, because bellows 6 contracts and valve element 9 operates in its closing direction, the pressure in crank chamber 65 is reduced, and the displacement for discharge is increased by decrease of a pressure difference between crank chamber 55 and suction chamber 65. Thus, in a case of a constant electromagnetic force, the opening degree of valve element 9 is adjusted so that the pressure in the suction chamber becomes a predetermined value, and the displacement for discharge is controlled.
In the above-described displacement control, because gap 14 formed at the through portion of valve element 9 in partition wall 15 is formed as a flow passage, a non-contact structure may be easily formed between valve element 9 and partition wall 15 by setting a large clearance in this portion, and a sliding resistance is not generated in this portion. Further, in this embodiment, because gap 18 with a non-contact structure for giving no sliding resistance is formed also between transmission rod 13 of valve element 9 and fixed iron core 19, a sliding resistance is not generated also in this portion. Therefore, valve element 9 is supported movably by totally two sliding parts of a lower-end side sliding part between valve casing 2 and transmission rod 10 and an upper-end side sliding part between plunger 21 fixed to valve element 9 and tubular member 25. The number of sliding parts is greatly reduced as compared with totally four sliding parts in the conventional case, the sliding resistance is greatly decreased when valve element 9 is moved and controlled and a smooth movement of valve element 9 is ensured, and the opening and closing operation of valve part 11 is carried out at a high accuracy by well following the variation of the electromagnetic force or the suction pressure. Therefore, a more smooth and stable high-reliability control of displacement for discharge may become possible. Further, because valve element 9 is supported at upper and lower parts substantially with two-point suspension, the supporting formation for making a rod slide may become stable.
Further, because gap 14 between the inner circumferential surface of partition wall 15 and the outer circumferential surface of valve element 9 is formed as a fixed orifice, it is not necessary to provide the fixed orifice at another place, and as compared with the conventional structure, it becomes possible to simplify, in particular, the processing of the cylinder block and the vicinity thereof, and further, it is possible to simplify the processing of the compressor as a whole and to reduce the cost thereof.
In displacement control valve 31 thus constructed, although bellows 6 senses the pressure in the crank chamber, by enlarging the area for receiving the suction pressure of partition wall 32 moved together with valve element 9, the bellows operates to expand and contract substantially in response to the suction pressure, thereby moving and controlling valve element 9 in its axial direction, and a similar control to that in displacement control valve 1 depicted in
Also in this displacement control valve 31, valve element 9 is supported movably by totally two sliding parts of a lower-end side sliding part between valve casing 33 and transmission rod 10 and an upper-end side sliding part between plunger 21 fixed to valve element 9 and tubular member 25. The number of sliding parts is greatly reduced as compared with the conventional number and the sliding resistance is greatly decreased, and a smooth movement of valve element 9 is ensured, and a smooth and stable high-reliability control of displacement for discharge may become possible.
Further, because gap 34 between the outer circumferential surface of partition wall 32 and the inner circumferential surface of valve casing 33 is formed as a fixed orifice, it is not necessary to provide the fixed orifice at another place, and as compared with the conventional structure, it becomes possible to simplify, in particular, the processing of the cylinder block and the vicinity thereof, and further, it is possible to simplify the processing of the compressor as a whole and to reduce the cost thereof.
In the present invention, a variable displacement compressor suitable for use in an air conditioning system for vehicles, etc. can be provided, and especially, a variable displacement compressor, in which a smooth and high-reliability operation can be carried out at the portion of the displacement control valve and the processing of which can be simplified as a whole, may be provided.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2002-106461 | Apr 2002 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP03/04441 | 4/8/2003 | WO |
