Piston compressor for compressing gas

Abstract: A piston (21) for use in a compressor that compresses gas containing lubricating oil is disclosed. The compressor includes a housing (11, 12, 13) having a crank chamber (15) and cylinder bores (12a), and a swash plate (19) located in the crank chamber (15). The swash plate (19) is operably connected to the pistons (21) by shoes (22) to convert the rotation of a drive shaft (16) to the reciprocation of each piston (21). Each piston (21) has a head (21c) for compressing the gas supplied to the cylinder bore (12a) and a skirt (21a) projecting from the head (21c) toward the crank chamber (15). The skirt (21a) is connected to the swash plate (19). A restrictor (21e) is provided on the skirt (21a) to prevent the piston (21) from rotating in the cylinder bore (12a). The restrictor (21e) has a pair of arched surfaces (31) slidably contacting an inner surface of the housing (11, 12, 13) and a recessed surface (30) located between the arched surfaces (31) and free from contact with the inner surface. The recessed surface (30) defines a gap (S1) for allowing passage of the oil between the recessed surface (30) and the inner surface. The gap (S1) leads the oil in the crank chamber (15) toward the shoes (22) when the piston (21) moves from a top dead center position to a bottom dead center position.

Description: TECHNICAL FIELD TO WHICH THE INVENTION BELONGS The present invention relates to piston type compressors that convert rotation of a rotary shaft to linear reciprocation of a piston with a driving body such as a swash plate, and more particularly, to pistons used in such compressors. RELATED BACKGROUND ART Compressors are employed in air-conditioning systems for vehicles. Piston type compressors are used in such systems. A typical piston type compressor is provided with a driving body, such as a swash plate, to reciprocate pistons. The swash plate is supported by a drive shaft in a crank chamber and converts the rotation of the drive shaft to the linear reciprocation of each piston in an associated cylinder bore. The reciprocation of the piston draws refrigerant gas into the cylinder bore from a suction chamber, compresses the gas in the cylinder bore, and discharges the gas into a discharge chamber. The typical piston type compressor draws the refrigerant gas from an external refrigerant circuit into a suction chamber by way of the crank chamber. In such a compressor, in which the crank chamber constitutes a portion of a refrigerant gas passage, the refrigerant gas from the external refrigerant circuit passing through the crank chamber sufficiently lubricates various parts in the crank chamber, such as the piston and the swash plate, with the lubricating oil suspended in the gas. There is also a type of compressor that draws in refrigerant gas from an external refrigerant circuit without having the gas flow through its crank chamber. In such a compressor, the driving plate, or swash plate, is supported so that it inclines with respect to the drive shaft. The inclination of the swash plate changes in accordance with the difference between the pressure in the crank chamber and the pressure in the cylinder bores. The displacement of the compressor varies in accordance with the inclination of the swash plate. The difference between the pressure in the crank chamber and the pressure in the cylinder bores is changed, for example, by adjusting the pressure in the crank chamber using a control valve. Since the pressure of the crank chamber is adjusted to control the inclination of the swash plate in such type of compressor, the crank chamber is not included in the suction passage. Therefore, the various parts in the crank chamber are lubricated mainly by lubricating oil that is included in blowby gas. Blowby gas refers to the refrigerant gas in the cylinder bore that leaks into the crank chamber through the space defined between the outer surface of the piston and the wall of the associated cylinder bore when the piston compresses the refrigerant gas in the cylinder bore. The amount of blowby gas, or lubricating oil, supplied to the crank chamber is determined by the dimension of the clearance defined between the outer surface of the piston and the wall of the cylinder bore. Accordingly, it is necessary to increase the dimension of the clearance to supply a sufficient amount of lubricating oil for satisfactory lubrication of the various parts in the crank chamber. However, a large clearance between the piston and the cylinder bore degrades the compressing efficiency of the compressor. To cope with this problem, compressors such as that shown in Fig. 8 are known in the prior art. The compressor has a swash plate 100. The swash plate 100 is mounted on a drive shaft 104 in a crank chamber 103, which is provided between the cylinder block 101 and the front housing 102, and supported so as to rotate integrally with the shaft 104. Single-headed pistons 105 are each accommodated in a cylinder bore 101a, which is provided in the cylinder block 101. A skirt 105a projects from the rear side of each piston 105 (to the left as viewed in Fig. 8 ) toward the crank chamber 103. The skirt 105a is operably connected to the swash plate 100 by a pair of shoes 106. Each shoe 106 is slidably clamped between the skirt 105a and the swash plate 100. The rotation of the drive shaft 104 is converted to the linear reciprocation of the piston 105 in the cylinder bore 101a by means of the swash plate 100 and the shoes 106. An annular groove 107 extends along the outer surface of each piston 105. Lubricating oil applied to the wall of the cylinder bore 101a is collected in the groove 107 and guided toward the crank chamber 103 during reciprocation of the piston 105. The lubricating oil lubricates the connecting portion between the swash plate 100 and the piston 105. Accordingly, in compressors that employ pistons having such structure, the various parts in the crank chamber may be satisfactorily lubricated without enlarging the dimension of the clearance between the piston and the cylinder bore, or without reducing the compressing efficiency of the compressor. As shown in Figs. 8 and 9 , the skirt 105a of the piston 105 has an arched surface 105b, which is defined on the surface facing the inner surface of the front housing 102. The arched surface 105b slides against the inner surface of the front housing 102. The radius of curvature of the arched surface 105b is the same as that of the inner surface of the front housing 102. When the piston 105 reciprocates, the arched surface 105b slides against the inner surface of the front housing 102 and prevents the piston 105 from rotating about its axis. The arched surface 105b extends along the entire width of the skirt 105a that faces the inner surface of the front housing 102. However, it is difficult to accurately machine the entire arched surface 105b so that it has the same radius of curvature as the inner surface of the front housing 102. Furthermore, the entire arched surface 105b, which extends for a wide range, slides against the inner surface of the front housing 102. Thus, when the piston 105 moves from the top dead center position to the bottom dead center position, the lubricating oil on the end face of the skirt 105a and the lubricating oil that collects at the bottom of the crank chamber 103 is dispersed toward the left, as viewed in Fig. 8 . The lubricating oil is not guided to the connecting portion between the piston 105 and the swash plate 100. Accordingly, this oil is not used efficiently, and the connecting portions between the pistons 105 and the swash plate 100 are not lubricated to the degree that is desirable. Further, it is referred to JP 06-346844 A which discloses a variety of piston rotation regulating structures for a swash plate type compressor. Among others, Fig. 7 shows a double head piston having a base integrated with a back surface of a neck of the piston. The base is U-shaped and includes two sliding portions spaced from one another by a predetermined circumferential distance and slidably contacting the inner surface of the compressor housing for regulating piston rotation, and a flat recessed portion connecting the sliding portions and free from contact with the inner wall of the housing. The upper surface of the sliding portions have a curvature larger than that of the inner surface of the housing, so that the sliding portions make line contact with the inner surface of the housing. DISCLOSURE OF THE INVENTION It is an objective of the present invention to provide a compressor having a piston that facilitates machining and effectively lubricates the joints connecting the piston to the driving body with the lubricating oil from the crank chamber. To achieve the above objective, the present invention provides a compressor as defined in claim 1. The dependent claims relate to further developments of the invention. BRIEF DESCRIPTION OF THE DRAWINGS The features of the present invention are set forth with particularity in the appended claims. The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which: Fig. 1 is a cross-sectional view showing a compressor employing pistons according to an example outside the present invention; Fig. 2 is an enlarged perspective view showing the piston of Fig. 1 ; Fig. 3 is a perspective view showing the piston located at the bottom dead center position; Fig. 4 is a schematic view illustrating the position of the linear groove with respect to the piston; Fig. 5 is an enlarged partial front view showing the skirt of the piston; Fig. 6 is a partial front view showing the skirt of a piston according to a further example outside the present invention; Fig. 7 is a partial front view showing the skirt of a piston according to an embodiment of the present invention; Fig. 8 is a partial cross-sectional view showing a prior art compressor; and Fig. 9 shows a cross-sectional view taken along line 9-9 in Fig. 8 . DESCRIPTION OF SPECIAL EMBODIMENTS A compressor employing pistons according to an example outside the present invention will now be described with reference to Figs. 1 to 5 . As shown in Fig. 1 , a front housing 11 is secured to the front end of a cylinder block 12. A rear housing 13 is secured to the rear end of the cylinder block 12 with a valve plate 14 arranged in between. The front housing 11, the cylinder block 12, and the rear housing 13 constitute the compressor housing. A suction chamber 13a and a discharge chamber 13b are defined in the rear housing 13. The valve plate 14 is provided with suction valves 14a, discharge valves 14b, suction ports 14c, and discharge ports 14d. A crank chamber 15 is defined between the front housing 11 and the cylinder block 12. A drive shaft 16 extends through the crank chamber 15 and is rotatably supported by a pair of bearings 17 in the front housing 11 and the cylinder block 12. A lug plate 18 is fixed to the rotary shaft 16. A swash plate 19, which serves as a driving body, is supported in the crank chamber 15 by the drive shaft 16 so that it is slidable and inclinable with respect to the axis L1 of the shaft 16. The swash plate 19 is connected to the lug plate 18 by a hinge mechanism 20. The hinge mechanism 20 is constituted by a support arm 20a, which projects from the lug plate 18, and a pair of guide pins 20b, which are projected from the swash plate 19. The guide pins 20b slidably fit into a pair of guide bores 20c, which extend through the support arm 20a. The hinge mechanism 20 integrally rotates the swash plate 19 with the drive shaft 16. The hinge mechanism 20 also guides the inclination and movement of the swash plate 19 in the direction of the axis L1. A plurality of cylinder bores 12a extend through the cylinder block 12 about the drive shaft 16. A single-headed piston 21 is reciprocally retained in each cylinder bore 12a. The piston 21 includes a hollow head 21c, and a skirt 21c projecting from the rear end of the head 21c toward the crank chamber 15. A slot 21b facing the drive shaft 16 is provided in the skirt 21a. The slot 21b has a pair of . opposing walls. A concave seat 21d is defined in each wall to receive a shoe 22. Each shoe 22 has a spheric portion and a flat portion. The spheric portion of each shoe 22 is slidably received in each seat 21d. The peripheral portion of the swash plate 19 is slidably held in the slot 21b of each piston 21 between the flat portions of the associated pair of shoes 22. Each shoe 22 serves as a connecting member, which connects the piston 21 to the swash plate 19. The rotation of the drive shaft 16 is converted to the linear reciprocation of each piston 21 in the associated cylinder bore 12a. During the suction stroke, in which the piston 21 moves from the top dead center position to the bottom dead center position, the refrigerant gas in the suction chamber 13a is forced out of the associated suction port 14c and suction valve 14a and drawn into the cylinder bore 12a. During the compression stroke, in which the piston 21 moves from the bottom dead center position to the top dead center position, the refrigerant gas in the cylinder bore 12a is compressed and forced out of the bore 12a through the associated discharge port 14d and discharge valve 14b. A pressurizing passage 23 extends through the cylinder block 12, the valve plate 14, and the rear housing 13 to connect the discharge chamber 13b to the crank chamber 15. An electromagnetic valve, or displacement control valve 24, is provided in the rear housing 13 and arranged in the pressurizing passage 23. The control valve 24 includes a solenoid 24a, a body 24b, and an aperture 24c. When the solenoid 24a is excited, the body 24b closes the aperture 24c. When the solenoid is de-excited, the body 24b opens the aperture 24c. A pressure releasing passage 16a extends through the drive shaft 16. A pressure releasing bore 12b extends through the cylinder block 12 and the valve plate 14. The releasing passage 16a and the releasing bore 12b connects the crank chamber 15 to the suction chamber 13a. When the solenoid 24a is excited and the pressuring passage 23 is closed, the high-pressure refrigerant gas in the discharge chamber 13b is not sent to the crank chamber 15. In this state, the refrigerant gas in the crank chamber 15 flows into the suction chamber 13a through the releasing passage 16a and the releasing bore 12b. This causes the pressure of the crank chamber 15 to approach the low pressure of the suction chamber 13a. As a result, the swash plate 19 is moved to a maximum inclination position, as shown in Fig. 1 , and the displacement of the compressor becomes maximum. The swash plate 19 is restricted from inclining beyond the maximum inclination position by the abutment of a stopper 19a, which is provided on the front side of the swash plate 19, against the lug plate 18. When the solenoid 24a is de-excited and the pressurizing passage 23 is opened, the high-pressure refrigerant gas in the discharge chamber 13b is sent to the crank chamber 15. This increases the pressure of the crank chamber 15. As a result, the swash plate 19 is moved to a minimum inclination position and the displacement of the compressor becomes minimum. The swash plate 19 is restricted from inclining further beyond the minimum inclination position by the abutment of the swash plate 19 against a ring 25, which is fit to the drive shaft 16. As described above, the pressure of the crank chamber 15 is adjusted by exciting the solenoid 24a of the control valve 24 to close the pressurizing passage 23 or by de-exciting the solenoid 24a to open the pressurizing passage 23. When the pressure of the crank chamber 15 changes, the difference between the pressure acting on the rear surface of the piston 21 (to the left as viewed in Fig. 1 ) and the pressure acting on the front surface of the piston 21 (to the right as viewed in Fig. 1 ) is altered. The inclination of the swash plate 19 is altered in accordance with the pressure difference. This changes the stroke of the pistons 21 and varies the displacement of the compressor. As shown in Figs. 1 through 4 , each piston 21 has an annular groove 26, which extends in the circumferential direction along the cylindrical outer surface of the piston 21 near the top of the head 21c. As shown in Fig. 3 , the annular groove 26 is provided at a position where the groove 26 is not exposed to the inside of the crank chamber 15 when the piston 21 is located at the bottom dead center position. In Figs. 1 through 3 , the swash plate 9 is shown at the maximum inclination position. Each piston 21 also has a linear groove 27, which extends along the outer surface of the piston 21 parallel to the axis L2 of the piston 21. One end of the linear groove 27 is located at the vicinity of the annular groove 26. The linear groove 27 is located on the outer surface of the piston 21 at a position described below. As shown in Fig. 4 , when viewing the piston 21 so that the rotating direction R of the rotary shaft 6 is clockwise (in this drawing, the piston 21 is viewed from the skirt side), an imaginary straight line L3 extends intersecting the axis L1 of the drive shaft 16 and the axis L3 of the piston 21. Among the two intersecting points P1, P2 at which the straight line L3 and the outer surface of the piston 21 intersect, the position of the intersecting point P1, located at the farther side of the outer surface with respect to the axis L of the piston 21, is herein referred to as the twelve o'clock position. In this case, the linear groove 27 is located within a range E, which is defined between positions corresponding to nine o'clock and eleven o'clock on the outer surface of the piston 21. As shown in Fig. 1 , the position and length of the linear groove 27 is determined so that it is not exposed from the cylinder bore 12a to the inside of the crank chamber 15 when the piston 21 moves to the top dead center position. The linear groove 27 is not connected with the annular groove 26. The surface of the piston 21 is ground using a centerless grinding method. In the centerless grinding method, which is not shown, the workpiece, or piston 21, is held on a rest and ground by rotating the piston 21 together with a grinding wheel. The piston 21 is not held by a chuck. Therefore, if a plurality of linear grooves 27 are provided in the outer surface of the piston 21, the rotating axis of the piston 21 placed on the rest becomes unstable. This hinders precision grinding. Accordingly, it is preferable that the number of linear grooves 27 be minimized so as to enable accurate grinding when employing the centerless grinding method. In this embodiment, the piston 21 is provided with only a single linear groove 27, the width and depth of which are minimized but are sufficient to supply lubricating oil to the crank chamber 15. As shown in Figs. 1 , 2 , and 5 , a substantially T-shaped restrictor 21e is provided on each piston 21 at the distal end of the skirt 21a. A sloped surface 28 extends along the edge of the end face of the restrictor 21e. When the piston 21 moves from the top dead center position to the bottom dead center position, the lubricating oil on the end face of the skirt 21a and the inner surface of the front housing 11, and the lubricating oil that collects at the bottom of the crank chamber 15 is guided along the sloped surface 28 toward the portion connecting the piston 21 and the swash plate 19, that is, toward the shoes 22. A recess 29 facing toward the inner surface of the front housing 11 extends along the skirt 21a adjacent to the restrictor 21e. The restrictor 21e has a flat portion 30, which is located at the middle of the surface facing the inner surface of the front housing 11. The restrictor 21e also has a pair of arched surfaces 31 serving to restrict rotation of the piston 21. One arched surface 31 extends from each side of the flat portion 30. The radius of curvature of the arched surfaces 31 is substantially the same as that of the inner surface of the front housing 11. The arched surfaces 31 are in surface contact with the inner surface of the front housing 11. A gap S1 is provided between the flat portion 30 and the inner surface of the front housing 11. During reciprocation of each piston 21, the arched surfaces 31 of the restrictor 21e slide against the inner surface of the front housing 11. This prevents the piston 21 from rotating about its axis L2. Furthermore, during the reciprocation of the piston 21, the lubricating oil in the crank chamber 15 is guided toward the recess 29 through the gap S1 between the flat portion 30 and the inner surface of the front housing 11. The lubricating oil is then sent to the connecting portion between the piston 21 and the swash plate 19, or the shoes 22. The operation of the compressor having the above structure will now be described. During the suction stroke, in which the piston 21 moves from the top dead center position to the bottom dead center position, the refrigerant gas in the suction chamber 13 is drawn into the associated cylinder bore 12a. Furthermore, some of the lubricating oil suspended in the refrigerant gas is applied to the wall of the cylinder bore 12a. During the discharge stroke, in which the piston 21 moves from the bottom dead center position to the top dead center position, the refrigerant gas in the cylinder bore 12a is compressed and discharged into the discharge chamber 13b. Furthermore, some of the refrigerant gas (blow-by gas) leaks into the crank chamber 15 through a clearance C1 provided between the outer surface of the piston 21 and the wall of the cylinder bore 12a. As the blow-by gas passes through the clearance C1, some of the lubricating oil suspended in the gas is applied to the wall of the cylinder bore 12a. The lubricating oil on the wall of the cylinder bore 12a is wiped off by the edge of the annular groove 26 in the piston 21 and collects in the groove 26. When the piston 21 undergoes the compression stroke, the blow-by gas that leaks out of the cylinder bore 12a increases the pressure in the annular groove 26. The linear groove 27 is closed entirely by the wall of the cylinder bore 12a only when the piston 21 is located in the vicinity of the top dead center position. If the piston 21 moves away from the top dead center position, at least a portion of the linear groove 27 becomes exposed to the inside of the crank chamber 15. This causes the pressure in the linear groove 27 to become equal to or slightly higher than the pressure of the crank chamber 15. The linear groove 27 is communicated with the annular groove 26 through the narrow clearance C1. Accordingly, when the piston 21 undergoes the compression stroke, the difference between the pressure in the annular groove 26 and the pressure in the linear groove 27 causes the lubricating oil in the annular groove 26 to move through the clearance C1 and enter the linear groove 27. The lubricating oil that enters the linear groove 27 then enters the crank chamber 15 when the linear groove 27 becomes exposed to the inside of the crank chamber 15. When the inclination of the swash plate 19 becomes small, the linear groove 27 does not move out of the cylinder bore 12a even if the piston 21 is at the bottom dead center position. However, in this example, the distance between the linear groove 27 and the skirt side end of the head 21c is short. This easily allows the lubricating oil in the linear groove 27 to move into the clearance C1 and enter the crank chamber 15. The lubricating oil that enters the crank chamber 15 is applied to the inner surface of the front housing 11 and collects at the bottom of the crank chamber 15. As each piston 21 moves from the top dead center position to the bottom dead center position during the suction stroke, the lubricating oil moves along the sloped surface 28, which is provided along the edge of the end face of the skirt 21a, to the connecting portion between the piston 21 and the swash plate 19, or the shoes 22. In addition, the lubricating oil, especially the oil on the inner surface of the front housing, is guided through the gap S1 between the flat portion 30 and the inner surface of the front housing 30 and enters the recess 29. The lubricating oil subsequently lubricates the connecting portion between the piston 21 and the swash plate 19. Accordingly, when each piston 21 undergoes the suction stroke, the lubricating oil on the end face of the skirt 21a and the inner surface of the front housing 11, and the lubricating oil that collects at the bottom of the crank chamber 15 is not dispersed by the movement of the end face of the skirt 21a. This causes more effective lubrication of the connecting portion between the piston 21 and the swash plate 19, which is one of the portions that definitely requires lubrication. As described above, the flat portion 30 is provided on a portion of the surface of the restrictor 21e that faces the inner surface of the front housing 11. The pair of arched surfaces 31, which come into surface contact with the inner surface of the front housing 11, extend from each side of the flat portion 30 with a predetermined interval therebetween. Therefore, the entire surface facing the front housing 11 need not be accurately machined to an arch having the same radius of curvature as the inner surface of the front housing 102. This facilitates the machining of the restrictor 21e. The flat portion 30, or recessed portion, provided between the pair of arched surfaces 31 forms a gap S1 between the inner surface of the front housing 11. Thus, when the piston 21 reciprocates, lubricating oil is . efficiently applied to the joint between the piston 21 and the swash plate 19 through the gap S1. The radius of curvature of the arched surfaces 31 is substantially the same as that of the front housing 11. This maximizes the contact area between the restrictor 21e and the inner surface of the front housing 11 regardless of the flat portion 30, which extends along the surface facing toward the inner surface of the front housing 11 but does not contact the inner surface. This further effectively prevents the piston 21 from rotating about its axis L2 and stabilizes the movement of the piston 21. The sloped surface 28 extends along the edge of the end face of the restrictor 21e. Thus, the lubricating oil on the inner surface of the front housing 11 is efficiently directed by the sloped surface 28 to the joint between the piston 21 and the swash plate 19. A further example outside the present invention will now be described with reference to Fig. 6 . In the second embodiment, there are three flat portions 30. One at the middle of the surface facing the inner surface of the front housing 11 and the other two on each side of the first one. A gap S1 is defined between each flat portion 30 and the inner surface of the front housing 11. These gaps S1 allow passage of the lubricating oil. The intersections between the middle flat portion 30 and the flat portions 30 on each side of the middle flat portion 30 form corners. Each corner, or contact portion 32, extends parallel to the axis L2 of the piston 21 and comes into linear contact with the front housing 11. In this embodiment, the contact portions 32 serve to restrict the rotation of the piston 21. When the piston 21 reciprocates, the contact portions 32 slide against the inner surface of the front housing 11 and prevent the piston 21 from rotating about its axis L2. Accordingly, the advantageous effects of the first example may be obtained in the second example. In the second embodiment, the restrictor 21e has a plurality of flat surfaces 30, which define a plurality of contact portions 32. The contact portions 32 come into linear contact with the inner surface of the front housing 11. Accordingly, the surface facing the inner surface of the front housing 11 need only be machined flat. It is not necessary to machine the surface in an arched manner. This further facilitates the machining of the restrictor 21e. In addition, the lubricating oil from the crank chamber 15 passes through the plurality of gaps S1 and lubricates the connecting portion between the piston 21 and the swash plate 19 further efficiently. An embodiment according to the present invention will now be described with reference to Fig. 7 . Like the first example, in the embodiment, the flat portion 30 is provided at the middle of the surface of the restrictor 21e facing the inner surface of the front housing 11. A pair of lips 33, which serve to restrict the rotation of the piston 21, is provided on the sides of the flat portion 30. The lips 33 extend parallel to the axis of the piston 21 and contact the inner surface of the front housing 11. When the piston 21 reciprocates, the lips 33 slide against the inner surface of the front housing 11 and prevents the piston 21 from rotating about its axis L2. The advantageous effects of the first and second example is also obtained in the embodiment. Furthermore, in this embodiment, the lips 33 form a large gap S1 between the flat portion 30 and the inner surface of the front housing 11 to allow passage of the lubricating oil. Thus, when the piston 21 reciprocates, the lubricating oil from the crank chamber 15 passes through the large gap S1 and lubricates the joint between the piston 21 and the swash plate 19 further efficiently. Although one embodiment of the present invention has been described so far, it should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention. More particularly, the present invention may be modified as described below. In the embodiment, the flat portion 30 defines the gap S1 between the restrictor 21e and the inner surface of the front housing 11. However, instead of using the flat portion 30, a groove provided in the restrictor 21e may be used to define the gap S1. Therefore, the present embodiment is to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope of the appended claims.

Claims: A compressor for compressing gas containing lubricating oil, wherein the compressor includes: a compressor housing having a front housing (11) secured to the front end of a cylinder block (12) and a rear housing (13) secured to the rear end of the cylinder block (12) with a valve plate (14) arranged between the rear housing (13) and the cylinder block (12), a crank chamber (15) being defined between the inner surface of the front housing (11) and the cylinder block (12), and a cylinder bore (12a) that accommodates a piston (21) extending through the cylinder block (12), a driving body (19) located in the crank chamber (15) and operably connected to the piston (21) by a connecting joint (22), wherein the driving body (19) reciprocates the piston (21) between a top dead center position and a bottom dead center position by means of the connecting joint (22), wherein the piston (21) has a hollow head (21c) for compressing the gas supplied to the cylinder bore (12a), a skirt (21a) projecting from the hollow head (21c) toward the crank chamber (15) and connected to the driving body (19), and a restrictor (21e) provided on the skirt (21a) to prevent the piston (21) from rotating in the cylinder bore (12a)wherein the restrictor (21e) has a plurality of sliding portions (33) which come into contact with the inner surface of the front housing (11), each sliding portion (33) including a raised portion (33) in the form of a lip extending along an axis (L2) of the piston (21) and being spaced from one another by a predetermined circumferential distance to form a recessed portion (30) located between the raised portions (33) and free from contact with the inner surface of the front housing (11), characterized in that said recessed portion (30) and the inner surface of the front housing (11) define a gap (S1) that leads lubricating oil in the crank chamber (15) from an end face of the restrictor (21e) toward a recess (29) which is located between the restrictor (21e) and the hollow head (21c) to define a space for allowing passage of the lubricating oil between the skirt (21a) and the inner surface of the front housing (11), for the lubricating oil to enter the recess (29) and lubricate the connecting joint (22) when the piston (21) moves from the top dead center position to the bottom dead center position. The compressor according to claim 1, wherein the piston (21) has a sloped surface (28) which extends along an edge of the end face of the restrictor (21e) and guides lubricating oil in the crank chamber (15) to the connecting joint (22) when the piston (21) moves from the top dead center position to the bottom dead center position. The compressor according to claim 1 or 2, wherein the piston (21) has an annular groove (26) which extends in a circumferential direction along a cylindrical outer surface of the piston (21) near the top of the hollow head (21c). The compressor according to claim 3, wherein the piston (21) has a linear groove (27) which extends along an outer surface of the piston (21) parallel to an axis (L2) of the piston (21), one end of the linear groove (27) being located in the vicinity of the annular groove (26) and the position and length of the linear groove (27) being determined so that the linear groove (27) is not exposed from the cylinder bore (12a) to the inside of the crank chamber (15) when the piston (21) moves to the top dead center position. The compressor according to any one of the preceding claims, wherein the recessed portion includes a flat surface (30). The compressor according to any one of claims 1 to 5, further including: a drive shaft (16) for tiltably supporting the driving body (19) that includes a swash plate, wherein the inclination of the driving body (19) varies in accordance with the difference between the pressure in the crank chamber (15) and the pressure in the cylinder bore (12a), and wherein the piston (21) moves by a stroke based on the inclination of the driving body (19) to control the displacement of the compressor; and means (24) for adjusting the difference between the pressure in the crank chamber (15) and the pressure in the cylinder bore (12a). The compressor according to any one of claims 1 to 5, further including: a drive shaft (16) for supporting the driving body (19) that includes a swash plate; and a pair of shoes (22) included in the connecting joint and received in the skirt (21a) of the piston (21) to slidably hold the driving body (19).

Inventors: HIRAMATSU OSAMU, HOSHIDA TAKAHIRO, KANZAKI SHIGEKI, MURAO KAZUSHIGE, HIRAMATSU, OSAMU, HOSHIDA, TAKAHIRO, KANZAKI, SHIGEKI, MURAO, KAZUSHIGE
Applicants: TOYOTA JIDOSHOKKI KK, KABUSHIKI KAISHA TOYOTA JIDOSHOKKI
Application year: 1997
Main classification: F04B27
IPC codes: F04B27