JP4616090B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor, and more particularly to a compressor that can be used in an air conditioner such as an automobile to compress a fluid.

  2. Description of the Related Art Conventionally, a compressor used in an air conditioner such as an automobile includes a fixed scroll fixed to a housing and a movable scroll arranged so as to mesh with the fixed wrap, and the movable through an eccentric drive pin. A scroll type compressor that compresses fluid between the fixed scroll and the movable scroll by turning the scroll, and a piston fitted to the swash plate reciprocate in the cylinder as the swash plate rotates. There is known a swash plate type compressor that compresses the fluid.

  For example, as such a scroll compressor, as disclosed in Patent Document 1, a movable scroll and a fixed scroll are disposed inside a front housing, and the fixed scroll is connected to an end portion of the front housing. Fixed to the rear housing. Then, the refrigerant compressed by the movable scroll and the fixed scroll is introduced from the compression chamber to the separation chamber provided with the separation pipe through the introduction hole of the rear housing, and the refrigerant and the lubricating oil contained in the refrigerant are separated. Is done. The lubricating oil is discharged to the oil storage chamber through the discharge hole, and the compressed fluid is discharged from the outlet through the discharge chamber.

JP 11-82352 A

  By the way, in the prior art which concerns on patent document 1, although the separation pipe for separating a refrigerant | coolant and lubricating oil is provided in the separation chamber, the said separation pipe is high-pressure in a compression chamber via a discharge chamber. When the compressed fluid is introduced into the separation chamber, a large pressing force is applied by the pressure, so that the separation pipe is required to have a predetermined strength. Further, the separation tube needs to be firmly fixed to the rear housing or the like so as to withstand the high-pressure compressed fluid, and it is necessary to provide fixing means for fixing the separation tube.

  However, as the strength of the separation tube is increased, its manufacturing cost increases, the assembly work when fixing via the fixing means is complicated, and the assembly property of the separation tube is increased. There is a problem that the production efficiency is lowered.

  The present invention has been made in consideration of the above-described various problems, and a compressor capable of reducing cost and improving assembly by adopting a separation pipe having a simple configuration. The purpose is to provide.

To achieve the above object, the present invention comprises a first housing and a second housing joined to the first housing via a gasket, and the compressed fluid is led out in the second housing. A compressor including a discharge chamber, a separation chamber that communicates with the discharge chamber and separates lubricating oil contained in the fluid, and an oil storage chamber that communicates with the separation chamber and stores the lubricating oil ,
A dividing wall formed in the second housing and extending along an axial direction of the second housing to divide the discharge chamber and the separation chamber, respectively;
An oil separation member having a pipe portion inserted into the separation chamber and a flange portion formed at an end of the pipe portion, and distributing the fluid and lubricating oil in the separation chamber;
A gasket having a sealing portion for sealing the separation chamber;
With
The oil separation member is integrally held by the gasket through the flange portion.

  According to the present invention, the oil separation member provided between the first housing and the second housing is integrally held by the gasket disposed between the first housing and the second housing, thereby fixing the oil separation member. The fixing means is not necessary, and the work can be easily performed by assembling the gasket, in which the oil separating member is pre-assembled, to the first housing and the second housing. For this reason, it is possible to improve the assembling property of the oil separation member in the compressor and to fix the oil separation member used in the prior art with a simple configuration of holding the oil separation member integrally with the gasket. Since the means can be made unnecessary, the number of parts can be reduced and the cost can be reduced.

  The oil separation member includes first and second fitting portions that are provided to face each other with a gasket interposed therebetween, and the first fitting portion and the second fitting portion are fitted to sandwich the gasket. It is good to hold it. Accordingly, the first and second fitting portions constituting the oil separation member are arranged to face each other with the gasket interposed therebetween, and the gasket is sandwiched between the first and second fitting portions, whereby the gasket is sandwiched between the first and second fitting portions. The oil separation member can be reliably and simply joined.

  Further, each of the first and second fitting portions is formed in a cylindrical shape having a flange portion having an enlarged diameter, and the first fitting portion is formed to have a smaller diameter than the second fitting portion, and the first fitting is performed. The second fitting portion may be fitted to the outer peripheral side of the portion, and the gasket may be sandwiched between the flange portions of the first and second fitting portions.

  Thus, what is necessary is just to satisfy | fill desired intensity | strength in the state by which the said 1st and 2nd fitting part was fitted by comprising the oil separation member from the 1st and 2nd fitting part fitted to each other. Therefore, the strength of each of the first and second fitting portions can be set small. Therefore, for example, the first and second fitting portions can be formed from an inexpensive press material, and as a result, the manufacturing cost of the oil separation member can be reduced.

  Further, by overlapping the fitting portions in the first and second fitting portions, the strength at the portions can be further improved, and the gasket is sandwiched via the flange portion, so that the flange portion allows oil to be Sealing between the separating member and the gasket can be suitably performed.

  Furthermore, the compressor may be a scroll type compressor that includes a movable scroll and a fixed scroll that functions as the first housing, and compresses fluid under a turning action of the movable scroll with respect to the fixed scroll. Thereby, even when the fluid compressed under the swirling action of the movable scroll is introduced into the separation chamber, the oil separation member is firmly fixed to the gasket, and its strength is sufficiently secured, Lubricating oil in the fluid can be reliably separated without being affected by pressure in the fluid.

  Furthermore, the compressor includes a valve plate that functions as the first housing, a piston that is displaceable along the axial direction, and a swash plate that is fitted with an inclination with respect to the axial line of the piston. The reciprocating compressor may compress the fluid by displacing the piston under the rotational action of the swash plate. Thereby, even when the fluid compressed under the rotating action of the swash plate is introduced into the separation chamber, the oil separation member is firmly fixed to the gasket, and its strength is sufficiently secured, Lubricating oil in the fluid can be reliably separated without being affected by pressure in the fluid.

  According to the present invention, the following effects can be obtained.

  That is, by fixing the oil separation member provided in the separation chamber integrally with the gasket disposed between the first housing and the second housing, a fixing means for fixing the oil separation member is unnecessary. In addition, the simple structure of holding the oil separation member integrally with the gasket can improve the assembly of the oil separation member in the compressor and reduce the number of parts compared to the conventional technology. To reduce costs.

  A preferred embodiment of the compressor according to the present invention will be described in detail below with reference to the accompanying drawings.

  In FIG. 1, reference numeral 10 indicates a scroll type compressor that functions as a compressor according to the first embodiment of the present invention.

  As shown in FIG. 1, the scroll compressor 10 includes a front housing 12 formed in a cup shape, and a rear housing (second housing) 14 connected to the front housing 12.

  In the upper part of the front housing 12, for example, a suction port 16 for introducing a fluid made of a refrigerant gas or the like into the inside thereof is formed. On the other hand, at the upper part of the rear housing 14, a discharge port 18 is formed for discharging the compressed fluid obtained by compressing the fluid by the scroll compressor 10 to, for example, a refrigerant circulation system. The front housing 12 and the rear housing 14 are provided with a plurality of attachment portions 20 for attaching the scroll compressor 10 to, for example, an engine or an external device.

  Inside the front housing 12, a fixed scroll (first housing) 22 and a movable scroll 24 that turns with respect to the fixed scroll 22 are inserted from the opened one end side.

  The fixed scroll 22 includes a fixed-side substrate portion 26 sandwiched between the front housing 12 and the rear housing 14, and a fixed-side spiral wall 28 erected in a spiral shape from the fixed-side substrate portion 26 toward the movable scroll 24. It consists of.

  As shown in FIGS. 2 and 3, the fixed-side spiral wall 28 is formed so that the wall thickness gradually increases in the radially outward direction from the outermost peripheral end of the fixed-side spiral wall 28 toward the inner peripheral end. Thus, the portion that is vertically upward in the scroll compressor 10 is formed to be the thickest. In the upper part of the fixed-side spiral wall 28, a guide passage 30 that is recessed in a radially inward direction is formed.

  The guide passage 30 is formed in a substantially rectangular shape in cross section and substantially in parallel with the axis of the fixed scroll 22, and an oil supply hole 32 is formed in the fixed side substrate portion 26 facing the guide passage 30. The oil supply hole 32 communicates with a supply passage 34 penetrating the fixed-side substrate portion 26, and communicates with the back surface 22a side of the fixed scroll 22 through the supply passage 34 (see FIG. 4). Further, the guide passage 30 is formed with a set of dam walls 36 erected outward in the radial direction on both sides of the guide passage 30 (see FIG. 3). The supply passage 34 is also formed substantially in parallel with the axis of the fixed scroll 22 like the guide passage 30. Thus, when lubricating oil (for example, oil) is supplied from the rear housing 14 side to the supply passage 34, the lubricating oil is discharged to the guide passage 30 through the oil supply hole 32, and the blocking wall Since the flow is prevented by 36 from flowing in the circumferential direction of the fixed spiral wall 28, it flows along the guide passage 30.

  On the other hand, as shown in FIGS. 1 and 2, the rear housing 14 is mounted on the back surface 22 a of the fixed side substrate portion 26 in the fixed scroll 22 via a gasket 38 formed in a thin plate shape. A lead-out hole 42 communicating with a discharge chamber 40 (described later) formed between the compression chamber 110 and the rear housing 14 is formed in a substantially central portion of the back surface 22a.

  A discharge valve 44 that closes the outlet hole 42 and bends and opens when the fluid compressed in the compression chamber 110 reaches a predetermined pressure is formed on the back surface 22a of the fixed scroll 22, and the discharge valve. A retainer 46 for restricting the valve opening of 44 is provided. One end of the discharge valve 44 is disposed at a position facing the lead-out hole 42, and the other end is fixed to a straight line spaced apart from the lead-out hole 42 by a predetermined distance via a bolt 48 with a retainer 46. (See FIGS. 5 and 6). The discharge valve 44 is seated so as to close the outlet hole 42, and the discharge valve 44 is separated from the outlet hole 42 by the pressure of the compressed fluid introduced into the outlet hole 42, so that the fluid passes through the outlet hole 42. It is supplied to the discharge chamber 40.

  Since the retainer 46 is inclined at a predetermined angle in a direction away from the back surface 22a with the end fixed by the bolt 48 as a base point, the discharge valve 44 is opened by the compressed fluid led out through the lead-out hole 42. When this happens, the discharge valve 44 comes into contact with the retainer 46 and its valve opening is regulated.

  Further, as shown in FIGS. 5 and 6, the supply passage 34 opened to the back surface 22 a of the fixed scroll 22 is formed in an upper portion of the back surface 22 a and is arranged substantially in line with the outlet hole 42. The back surface 22a is formed between the lead-out hole 42 and the supply passage 34, and is recessed by a predetermined depth. The first recess 50 is adjacent to the first recess 50, and an oil separation pipe (oil separation member). ) 52 is disposed, and third and fourth recesses 56 and 58 formed on the lower side of the back surface 22a. In addition, the 1st-4th recessed parts 50, 54, 56, and 58 are depressed by substantially the same depth from the surface of the back surface 22a.

  The first recess 50 is formed substantially parallel to the discharge valve 44 and the retainer 46 and is formed at a position facing the discharge chamber 40 of the rear housing 14.

  The second recess 54 is disposed at a position that is substantially symmetric with the first recess 50 with respect to a vertical line passing through the center of the outlet hole 42, and extends in the vertical direction of the back surface 22 a to separate the rear housing 14. 62 and a discharge chamber 64 (described later). An oil separation pipe 52 is attached to one end of the second recess 54 on the lead-out hole 42 side via a circular recess 60 formed in a substantially circular shape (see FIG. 7). The depth D1 of the second recess 54 is set slightly deeper than the depth D2 of the circular recess 60 (D1> D2) (see FIG. 8).

  As shown in FIGS. 6 and 7, the oil separation pipe 52 is formed in a cylindrical portion 66 (first fitting portion) formed in a cylindrical shape and an end portion of the cylindrical portion 66, and is radially outward. And a disk-shaped flange portion 68 whose diameter is increased. The cylindrical portion 66 is connected eccentrically with respect to the center of the disc-shaped flange portion 68, and a passage 70 penetrating in the axial direction is formed inside the cylindrical portion 66 and the flange portion 68.

  The flange portion 68 is formed with an engagement groove 72 that is recessed in a substantially triangular shape in the radial inward direction from the circumferential surface thereof. When the oil separation pipe 52 is attached to the circular recess 60, the engagement groove 72 is formed. The groove 72 engages with an engaging protrusion 74 formed in the circular recess 60. Accordingly, the oil separation pipe 52 is positioned with respect to the fixed scroll 22 and the rotational displacement of the flange portion 68 in the circular recess 60 is restricted. In other words, the engagement protrusion 74 formed in the circular recess 60 functions as a detent for the oil separation pipe 52.

  Further, the flange portion 68 is formed with a groove portion 76 that is recessed toward the tube portion 66 on the surface facing the circular recess portion 60. When the flange portion 68 is inserted into the circular recess portion 60, the groove portion 76 is 2 faces the recess 54 (see FIG. 8). In other words, the passage 70 of the oil separation pipe 52 and the second recess 54 communicate with each other through the groove 76.

  The oil separation pipe 52 is configured such that the gasket 38 is brought into contact with the back surface 22a of the fixed scroll 22 with the flange portion 68 inserted into the circular recess 60, and the rear housing 14 is brought into contact with the gasket 38. The oil separation pipe 52 is sandwiched and held between the fixed scroll 22 and the rear housing 14.

  Instead of providing the engagement groove 72 of the oil separation pipe 52 and the engagement protrusion 74 of the circular recess 60 described above, the flange 68 of the oil separation pipe 52a shown in FIG. It may be fixed at 78. As a result, the oil separation pipe 52 is held in a state of being positioned with respect to the fixed scroll 22, and the oil separation pipe 52 is more reliably secured by the clamping force by the fixing bolt 78 and the clamping force by the fixed scroll 22 and the rear housing 14. Fixed to.

  As shown in FIG. 6, the third recess 56 is disposed at a position that is substantially symmetrical with the second recess 54 with the lead-out hole 42 as the center, and the discharge chamber 40 of the rear housing 14 is similar to the first recess 50. It is formed in the position which opposes.

  The fourth recess 58 is arranged at a position that is in line with the discharge valve 44 and the retainer 46 and is formed at a position facing an oil storage chamber 80 (described later) of the rear housing 14.

  Between the circular recessed part 60 and the 4th recessed part 58 in the 2nd recessed part 54, the 1st communicating path 82 is formed substantially parallel to the discharge valve 44 and the retainer 46, and the said 1st communicating path 82 is predetermined from the back surface 22a. It is formed in a substantially straight line with a depth. When the fixed scroll 22 is assembled to the rear housing 14, one end of the first communication passage 82 faces the supply passage 34 communicating with the separation chamber 62 of the rear housing 14, and the other end is oil storage. It arrange | positions so that the chamber 80 may be opposed.

  A second communication passage 84 is formed below the fourth recess 58 so as to be substantially orthogonal to the axes of the discharge valve 44 and the retainer 46, and the second communication passage 84 is substantially the same as the first communication passage 82. It is formed in a substantially straight line indented to a depth of. When the fixed scroll 22 is assembled to the rear housing 14, one end portion of the second communication passage 84 faces a filter chamber 88 (described later) in which the filter 86 is mounted, and the other end portion is the rear housing. 14 is disposed so as to face an end portion of an oil supply groove 90 (described later) formed in 14.

  Further, a plurality of (for example, four locations) first bolt holes 92 are formed in the vicinity of the outer peripheral portion of the fixed scroll 22 at a predetermined interval, and a plurality of (for example, four) first bolt holes 92 are inserted through the first bolt holes 92. The bolt 94 is screwed into the screw hole 100 of the front housing 12 through the second bolt hole 96 of the gasket 38 and the third bolt hole 98 of the rear housing 14. As a result, the fixed scroll 22 is integrally fixed to the rear housing 14 and the front housing 12. At this time, an O-ring 102 is attached to the fixed-side substrate portion 26 of the fixed scroll 22 through an annular groove, and the suction chamber 104 formed by the fixed scroll 22 and the front housing 12 is sealed by the O-ring 102. Thus, airtightness is maintained (see FIG. 1).

  As shown in FIG. 1, the movable scroll 24 is erected in a spiral shape from the movable side substrate portion 106 to the fixed scroll 22 side from the movable side substrate portion 106, and engages with the fixed side spiral wall 28. And a spiral wall 108.

  A compression chamber 110 is formed by the fixed-side substrate portion 26 and the fixed-side spiral wall 28 in the fixed scroll 22 and the movable-side substrate portion 106 and the movable-side spiral wall 108 in the movable scroll 24.

  In order to seal the compression chamber 110, seal members 112 are slidably contacted with the movable side substrate portion 106 and the fixed side substrate portion 26 at the respective ends of the fixed side spiral wall 28 and the movable side spiral wall 108. It is installed.

  Further, when the movable side substrate portion 106 abuts on the fixed side spiral wall 28, the end portion of the guide passage 30 of the fixed scroll 22 is closed by the movable side substrate portion 106, and the guide passage 30 and the movable side substrate portion 106 are closed. It functions as an oil storage tank 114 in which a predetermined amount of lubricating oil is stored (see FIG. 4).

  A shaft portion 118 that is one end of the rotating shaft 116 is inserted into the other end portion of the front housing 12. The shaft portion 118 is rotatably supported via a first bearing 120 held at the other end of the front housing 12. A sealing member 122 for sealing the suction chamber 104 is fitted into the shaft portion 118 of the rotating shaft 116. The sealing member 122 is supported by an opening shoulder portion of the front housing 12, and is configured, for example, by covering a ring-shaped core made of a metal material with a rubber material or a resin material.

  On the other hand, the other end of the rotating shaft 116 is provided with a support 124 having a diameter larger than that of the one end. The support body 124 is rotatably supported by inserting an outer peripheral surface of the support body 124 into a second bearing 126 held by the front housing 12. A pin 128 eccentric to the axis is fixed to the support 124. That is, the rotating shaft 116 is rotatably supported by the first and second bearings 120 and 126.

  A mounting hole 130 opened toward the second bearing 126 side is formed in the movable side substrate portion 106 of the movable scroll 24, and a bush 134 is rotatably supported in the mounting hole 130 via a swivel bearing 132. ing. The bush 134 is formed with a hole 136 that is eccentric with respect to the axis thereof, and the pin 128 of the support 124 is inserted into the hole 136.

  An annular groove is formed at the tip of the pin 128, and a locking ring 138 is fitted into the annular groove. Accordingly, the axial movement of the pin 128 relative to the bush 134 is restricted by the locking ring 138 mounted in the annular groove. Further, a disc-shaped balance weight 140 is mounted near the base of the bush 134.

  Inside the front housing 12, there is a thrust plate 142 that slidably supports the movable scroll 24 by a sliding contact surface, and an Oldham ring that restricts the rotation of the movable scroll 24 and allows the movable scroll 24 to turn. 144, and the Oldham ring 144 is supported so as to be reciprocally displaceable in one direction orthogonal to the axis of the rotating shaft 116, and the axial thrust force applied to the movable scroll 24 is transmitted via the thrust plate 142. An Oldham base 146 to be received is disposed.

  A pair of first engaging recesses 148 that allow the movable scroll 24 to reciprocate only in the radial direction are formed on the front side of the movable side substrate 106 in the movable scroll 24. A pair of first engagement protrusions 150 protruding in the radial direction of the Oldham ring 144 are slidably engaged with the first engagement recess 148.

  Further, in order to allow the movable scroll 24 to reciprocate only in the direction orthogonal to the first engagement recess 148, the Oldham ring 144 has a diameter orthogonal to the first engagement protrusion 150. A pair of second engaging protrusions (not shown) protruding in the direction are formed. The pair of second engaging convex portions are slidably engaged with a pair of second engaging concave portions (not shown) protruding in the radial direction of the Oldham base 146.

  Further, the Oldham base 146 is fastened by a plurality of (for example, two) bolts 154 via the shim 152. This shim 152 is mounted to adjust the axial gap between the fixed scroll 22 and the movable scroll 24 to a predetermined value. When the gap is appropriately adjusted, the shim 152 It is not necessary to wear it.

  A pulley 158 is attached to the other end portion of the front housing 12 via a third bearing 156 on the outer peripheral portion thereof. A rotational force is transmitted to the pulley 158 from a rotational drive source such as an engine (not shown), and the rotational force is transmitted to the rotating shaft 116 by an on / off operation of an electromagnetic clutch 160 disposed in the pulley 158 or Detachment is performed.

  As shown in FIG. 2, a pair of first positioning holes 162 are formed on the end surface of the front housing 12 at a predetermined interval in a diagonal line. In the first positioning hole 162, a pair of positioning pins 164 are inserted and fixed at predetermined positions in the axial direction thereof. The positioning pin 164 functions as a positioning reference when the front housing 12, the fixed scroll 22, the gasket 38, and the rear housing 14 are assembled.

  That is, a pair of penetrating second positioning holes 166 are formed in the fixed scroll 22 corresponding to the positioning pins 164, and a pair of third positioning holes 168 are formed in the rear housing 14. 38 is formed with a pair of penetrating fourth positioning holes 170.

  Note that the positioning pin 164 may be inserted in advance into the second positioning hole 166 through which the fixed scroll 22 passes, or may be inserted into the third positioning hole 168 of the rear housing 14 and fixed in advance.

  As shown in FIG. 1, the rear housing 14 is connected to the front housing 12 via a fixed scroll 22 and a gasket 38. The rear housing 14 is sandwiched between a fixed scroll 22 and a gasket 38. As shown in FIGS. 5 and 10, the rear housing 14 is opened to the joint surface 172 side where the gasket 38 abuts, and is compressed in the compression chamber 110. A discharge chamber 40 into which the fluid is introduced; a separation chamber 62 that communicates with the discharge chamber 40 and separates the lubricating oil contained in the fluid; an oil storage chamber 80 in which the separated lubricating oil is stored; A discharge chamber 64 into which fluid is introduced after the lubricating oil is separated is formed.

  As shown in FIG. 2, in the rear housing 14, the discharge chamber 40 and the oil storage chamber 80 are separated by a first boundary wall (divided wall) 174, and the discharge chamber 40 and the discharge chamber 64 are separated by a second boundary. The oil storage chamber 80 and the discharge chamber 64 are separated by a third boundary wall (divided wall) 178 while being separated by a wall (divided wall) 176. The separation chamber 62 is separated from the discharge chamber 40, the oil storage chamber 80, and the discharge chamber 64 by an annular wall (partition wall) 180 formed around the separation chamber 62.

  As shown in FIG. 11, when the fixed scroll 22 is assembled to the rear housing 14, the discharge chamber 40 is positioned so as to face the lead-out hole 42, the first and third recesses 50, 56 of the fixed scroll 22. And is recessed by a predetermined depth along the axial direction of the rear housing 14. The discharge chamber 40 is formed on the joint surface 172 of the rear housing 14 so as to be about half the surface area. A discharge valve 44 and a retainer 46 are inserted into the discharge chamber 40.

  The separation chamber 62 is provided adjacent to the discharge chamber 40 and the discharge chamber 64 via the annular wall 180 and is formed at a position facing the oil separation pipe 52 when the fixed scroll 22 is assembled to the rear housing 14. (See FIG. 12). As shown in FIGS. 10 and 11, the separation chamber 62 has a substantially circular cross section and is formed at a predetermined depth along the axial direction of the rear housing 14. The separation chamber 62 is formed with first and second introduction passages 182 and 184 in which an annular wall 180 is notched between the separation chamber 62 and the discharge chambers through the first and second introduction passages 182 and 184. Forty fluids are introduced into the separation chamber 62. The first and second introduction passages 182 and 184 are formed at a predetermined interval so as to be substantially orthogonal to each other, and are formed so as to be tangential to the inner peripheral surface of the separation chamber 62. Therefore, the fluid introduced from the first and second introduction passages 182 and 184 into the separation chamber 62 flows in the separation chamber 62 while swirling along the inner peripheral surface thereof.

  Further, as shown in FIG. 12, the separation chamber 62 has a lead-out passage 186 formed in a bottom portion 62a spaced from the opening portion on the joint surface 172 side, and the lead-out passage 186 is formed along the axis of the separation chamber 62. It is inclined at a predetermined angle with respect to the joint surface 172. Specifically, the lead-out passage 186 has one end connected to a boundary portion with the inner peripheral surface that is vertically downward in the bottom 62a, and extends in a state inclined downward from the bottom 62a by a predetermined angle, The other end is open to the first boundary wall 174 of the joint surface 172 (see FIG. 10). That is, the inside of the separation chamber 62 and the joint surface 172 are in communication with each other through the outlet passage 186. The lead-out passage 186 is connected to the vicinity of the joint portion of the first boundary wall 174 with the annular wall 180.

  As shown in FIGS. 11 and 12, one end portion of the first communication passage 82 of the fixed scroll 22 faces the lead-out passage 186, and the other end portion of the first communication passage 82 faces the oil storage chamber 80. ing.

  Further, a cylinder portion 66 of the oil separation pipe 52 is inserted into the separation chamber 62, and a clearance 188 having a predetermined interval is provided between the cylinder portion 66 and the inner peripheral surface of the separation chamber 62. That is, the fluid introduced from the discharge chamber 40 to the separation chamber 62 flows to the bottom side through the clearance 188 and then flows to the flange portion 68 side of the oil separation pipe 52 through the passage 70 of the cylindrical portion 66. It circulates and is led out to the second recess 54 through the groove 76 of the oil separation pipe 52.

  The oil storage chamber 80 is provided on the lower side of the rear housing 14, and is formed at a position facing the fourth recess 58 of the fixed scroll 22 when the fixed scroll 22 is assembled to the rear housing 14.

  Further, as shown in FIG. 13, a filter chamber 88 to which a filter 86 capable of removing dust and the like in the lubricating oil is attached is provided at the lower portion of the oil storage chamber 80, and the filter chamber 88 is arranged in the axial direction. It is formed in a bottomed shape with a predetermined depth along. The filter chamber 88 is formed independently of the oil storage chamber 80.

  The filter 86 includes a filter member 190 formed in a cylindrical shape and having a mesh formed in a mesh shape, and a holding case 192 that holds the filter member 190 and attaches it to the filter chamber 88. As shown in FIG. 10, the lubricating oil communicates with the filter chamber 88 through a pair of third and fourth introduction passages 194 a and 194 b formed between the filter chamber 88 and the oil storage chamber 80. Then, when the lubricating oil passes from the outer peripheral side to the inner peripheral side of the filtering member 190, dust (for example, iron powder) contained in the lubricating oil is removed. At this time, the dust is held inside the filter chamber 88 formed in a bottomed shape.

  As shown in FIG. 13, the depth D3 of the third and fourth introduction passages 194a, 194b is formed shallower than the depth D4 along the axial direction of the filter chamber 88 (D3 <D4). The depth of the third and fourth introduction passages 194a, 194b on the oil storage chamber 80 side is formed shallower than the depth of the third and fourth introduction passages 194a, 194b on the filter chamber 88 side. This prevents dust or the like that has entered the filter chamber 88 from returning to the oil storage chamber 80 through the third and fourth introduction passages 194a and 194b, and the depth of the third and fourth introduction passages 194a and 194b. Since the filter chamber 88 side is formed deeper, the dust is guided to the filter chamber 88 side in the third and fourth introduction passages 194a and 194b, and the dust is suitably contained in the filter chamber 88. It becomes possible to collect.

  As shown in FIG. 10, the discharge chamber 64 is formed with a valve hole 64a communicating with the outside on the inner wall surface of the discharge chamber 64. The valve hole 64a discharges the fluid in the discharge chamber 64 to the outside. An open valve 89 is mounted. When the pressure of the fluid in the discharge chamber 64 becomes equal to or higher than a predetermined value, a valve body (not shown) provided in the release valve 89 is opened so that the fluid It is discharged to the outside through the open valve 89.

  Then, when the pressure in the discharge chamber 64 decreases to a desired pressure value, the valve body is closed again, the communication between the discharge chamber 64 and the outside is cut off, and the inside of the discharge chamber 64 The pressure is held at the desired pressure value. That is, the open valve 89 functions as a safety valve that prevents the pressure value in the discharge chamber 64 from becoming excessive.

  On the other hand, the joining surface 172 of the rear housing 14 extends along the outer peripheral portion of the discharge chamber 40 in the joining surface 172 from the vicinity of the filter chamber 88 in which the filter 86 is mounted, as shown in FIG. An oil supply groove 90 extending to the vicinity of the end of the second boundary wall 176 between the discharge chamber 40 and the discharge chamber 64 is formed. The oil supply groove 90 is formed to be recessed from the joint surface 172 by a predetermined depth. Further, as shown in FIG. 11, the oil supply groove 90 is a second communication path formed at one end portion on the back surface 22 a of the fixed scroll 22 when the fixed scroll 22 is assembled to the rear housing 14. A position opposite to one end portion of 84 and the other end portion faces the supply passage 34.

  That is, since the second communication passage 84 is connected to the center of the filter chamber 88 and the oil supply groove 90, the lubricating oil from which dust has been removed in the filter chamber 88 is supplied to the second communication passage 84. The oil flows from the passage 84 to the oil supply groove 90 and is supplied from the supply passage 34 to the oil supply hole 32.

  As shown in FIGS. 11 and 14, the gasket 38 is formed in a shape corresponding to the back surface 22 a of the fixed scroll 22 and the joint surface 172 of the rear housing 14, and is formed in a thin plate shape having a substantially constant thickness. .

  The gasket 38 includes a discharge opening 196 that opens in substantially the same shape as the discharge chamber 40 and an oil storage opening that opens in substantially the same shape as the oil storage chamber 80 when the gasket 38 is brought into contact with the joint surface 172 of the rear housing 14. 198, a discharge opening 200 formed at a position facing the discharge chamber 64, and a separation opening 202 formed at a position facing the separation chamber 62 and blocking a part of the separation chamber 62.

  A first partition 204 that closes a part of the discharge chamber 64 is formed at a portion adjacent to the discharge opening 200.

  The separation opening 202 is formed so that the cylindrical portion 66 of the oil separation pipe 52 is inserted, and the separation opening 202 has a second partition wall portion that closes the separation chamber 62 on the outer peripheral side of the cylindrical portion 66. (Sealing part) 206 is formed adjacently. Since the diameter of the separation opening 202 is formed to be approximately equal to the outer diameter of the cylindrical portion 66, the separation chamber 62 is closed by the second partition portion 206 after the cylindrical portion 66 is inserted.

  In addition, a filter opening 208 having a portion facing the center of the filter 86 is formed at a position facing the filter chamber 88, and a part of the filter chamber 88 is formed on the outer periphery of the filter opening 208. A third partition wall 210 that closes is formed. The third partition wall 210 is disposed so as to contact the end surface of the holding case 192 in the filter 86.

  Further, between the discharge opening 196 and the oil storage opening 198, a throttle hole 212 having a diameter smaller than the passage diameter of the outlet passage 186 is formed at a position facing the outlet passage 186 of the rear housing 14. That is, the outlet passage 186 communicates with the first communication passage 82 through the throttle hole 212 (see FIG. 12). The throttle hole 212 is formed, for example, by punching or the like on the gasket 38, and the diameter of the throttle hole 212 is arbitrarily set according to a desired flow rate to flow through the throttle hole 212.

  On the other hand, as shown in FIG. 14, a second bolt hole 96 facing the first bolt hole 92 of the fixed scroll 22 and the third bolt hole 98 of the rear housing 14 is formed in the outer peripheral portion of the gasket 38. An annular bead 214 is formed along the outer peripheral portion of the gasket 38 in the radially inward direction from the second bolt hole 96. This bead 214 slightly bulges in the axial direction of the gasket 38, and is formed at the inner peripheral side of the oil supply groove 90 in the rear housing 14, the first and second boundary walls 174 and 176, and the portion facing the annular wall 180, respectively. Has been. Thereby, when the gasket 38 is sandwiched between the fixed scroll 22 and the rear housing 14, the bead 214 can be reliably brought into contact with the fixed scroll 22 and the rear housing 14, It becomes possible to improve the sealing performance.

  The scroll compressor 10 according to the first embodiment of the present invention is basically configured as described above. Next, its operation and effects will be described.

  When the rotational force is transmitted to the rotary shaft 116 under the operation of the electromagnetic clutch 160, the support 124 rotates through the second bearing 126, and the pin 128 fixed to the support 124 thereby rotates the rotary shaft 116. It turns in a state that is eccentric with respect to the shaft center.

  Then, the bush 134 rotates through the pin 128 to slide the Oldham ring 144 and its rotation is restricted. Further, since the bush 134 is supported slidably by the sliding contact surface of the thrust plate 142, the movable scroll 24. Turns with respect to the fixed scroll 22 in a state where rotation is restricted.

  As a result, the compression chamber 110 formed between the fixed scroll 22 and the movable scroll 24 is gradually displaced from the outer peripheral portion to the central portion, and the fluid introduced into the suction chamber 104 under the sealing action of the seal member 112. Is gradually compressed. The compressed fluid is led out from the lead-out hole 42 to the discharge chamber 40 by separating the discharge valve 44 from the lead-out hole 42 under the pressure action.

  Next, the fluid is introduced from the discharge chamber 40 into the separation chamber 62 through the first and second introduction passages 182 and 184. At this time, since the fluid is introduced in a tangential direction with respect to the inner peripheral surface of the separation chamber 62, the inside of the clearance 188 between the cylindrical portion 66 of the oil separation pipe 52 and the inner peripheral surface is disposed on the inner peripheral surface. It circulates while turning along. As a result, the lubricating oil contained in the fluid is centrifuged from the fluid by the centrifugal force generated by the swirling flow of the fluid and separated to the inner peripheral surface side.

  The fluid from which the lubricating oil has been separated flows from the clearance 188 between the separation chamber 62 and the cylindrical portion 66 to the flange portion 68 side through the passage 70 of the oil separation pipe 52, and once the second recess of the fixed scroll 22. After being distributed to 54, it is introduced into the discharge chamber 64 of the rear housing 14. As a result, the fluid is discharged to a refrigerant circulation system (not shown) through the discharge port 18 communicating with the discharge chamber 64.

  On the other hand, as shown in FIG. 12, the lubricating oil separated from the fluid flows along the inner peripheral surface of the separation chamber 62 and then moves toward the joint surface 172 through the outlet passage 186 formed in the bottom 62a. The flow rate is reduced to a predetermined amount by the throttle hole 212 of the gasket 38 that flows and faces the outlet passage 186. Then, the oil is introduced and stored in the oil storage chamber 80 of the rear housing 14 through the first communication passage 82 of the fixed scroll 22 facing the throttle hole 212. At this time, since the flow rate of the lubricating oil introduced into the oil storage chamber 80 is reduced by the throttle hole 212 with respect to the flow rate flowing through the outlet passage 186, it can be gradually introduced into the oil storage chamber 80. Thus, the oil level of the lubricating oil in the oil storage chamber 80 can be always kept stable without disturbing the oil level.

  Next, the lubricating oil stored in the oil storage chamber 80 flows to the filter chamber 88 adjacent to the oil storage chamber 80 through a pair of third and fourth introduction passages 194a and 194b, and is provided in the filter chamber 88. The filter member 190 removes dust and the like contained in the lubricating oil. The dust and the like removed by the filter 86 remains inside the filter chamber 88, and thus the dust is prevented from entering the oil storage chamber 80 again.

  Then, the lubricating oil filtered by the filter 86 is supplied to the oil supply groove 90 of the rear housing 14 through the filter opening 208 and the second communication path 84 of the fixed scroll 22, and flows along the oil supply groove 90. As a result, the oil flows into the supply passage 34 connected to the other end of the oil supply groove 90.

  Finally, the lubricating oil is discharged from the supply passage 34 through the oil supply hole 32 into the guide passage 30 and flows along the guide passage 30 to the movable scroll 24 side. At this time, the sliding surface between the movable side substrate portion 106 and the fixed side spiral wall 28 of the movable scroll 24 is supplied, and the sliding surface is lubricated.

  Further, the lubricating oil is gradually stored in the oil storage tank 114 surrounded by the blocking walls 36 provided on both sides of the guide passage 30 and the movable side substrate portion 106 of the movable scroll 24 facing the guide passage 30. Surface height increases. Then, when the end surface of the movable side substrate portion 106 is displaced to a position lower than the oil level height under the turning action of the movable scroll 24 (see the two-dot chain line shape in FIG. 4), the lubricating oil is moved to the movable side. It passes over the board portion 106 and flows along the outer wall surface of the movable scroll 24 toward the bush 134 and the rotary shaft 116. Thereby, the bush 134, the rotating shaft 116, and the like are lubricated by the lubricating oil.

  Next, a modified example of the oil separation pipe 52 provided on the back surface 22a of the fixed scroll 22 will be described. The same components as those of the scroll compressor 10 according to the present embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 15, in the oil separation pipe (oil separation member) 250 according to the first modified example, a circular recess 252 into which the flange portion 68 of the oil separation pipe 250 can be inserted is provided on the rear housing 14 side. The gasket 38 is brought into contact with the end surface of the flange portion 68 in a state where the flange portion 68 is inserted into the circular recess 252 and is sandwiched between the rear housing 14 and the fixed scroll 22.

  With this configuration, there is no need to provide a fixing means for fixing the oil separation pipe 250 to the fixed scroll 22 or the rear housing 14, and the oil separation pipe 250 is disposed between the fixed scroll 22 and the rear housing 14. And can be held easily and reliably.

  In the oil separation pipe (oil separation member) 260 according to the second modification, the oil separation pipe 260 is formed integrally with the gasket 262 as shown in FIG. Specifically, a portion of the gasket 262 that faces the separation chamber 62 is projected in a cylindrical shape toward the separation chamber 62 side.

  With this configuration, the gasket 262 and the oil separation pipe 260 can be configured from a single component, so that the number of components in the scroll compressor 10 can be reduced, and the gasket 262 can be The oil separation pipe 260 can be reliably disposed at a position facing the separation chamber 62 only by a simple operation of being sandwiched between the fixed scroll 22 and the rear housing 14.

  Next, in the oil separation pipe (oil separation member) 270 according to the third modified example, as shown in FIG. 17, the cylinder portion 272 of the oil separation pipe 270 is lightly press-fitted into the separation opening 202 of the gasket 38. And fixed. Specifically, the cylindrical portion 272 has an enlarged diameter portion 274 whose outer diameter is slightly larger than the diameter of the separation opening 202 at the base portion, and the cylindrical portion 272 is directed toward the separation chamber 62 side. The enlarged diameter portion 274 is press-fitted into the separation opening 202 by pressing with the pressing force of.

  With this configuration, when the fixed scroll 22, the gasket 38, and the rear housing 14 are assembled, the enlarged diameter portion 274 of the oil separation pipe 270 is lightly press-fitted into the gasket 38 and temporarily fixed. There is no need to hold the oil separation pipe 270 in advance with respect to the fixed scroll 22 or the rear housing 14 by any holding means, and the oil separation pipe 270 can be further simplified when the fixed scroll 22 and the rear housing 14 are assembled. And it can install reliably.

  In the oil separation pipe (oil separation member) 280 according to the fourth modified example, as shown in FIG. 18, the tubular portion 66 is inserted from the fixed scroll 22 side into the separation opening 202 of the gasket 38, and the flange portion 68. Is engaged with the side surface of the gasket 38, and a fitting cylinder (second fitting part) 282 having an inner peripheral diameter substantially equal to the outer peripheral diameter of the cylindrical part 66 is rear housing with respect to the cylindrical part 66. Inserted from the 14th side, the fitting cylinder 282 and the cylinder portion 66 are fitted.

  With this configuration, the gasket 38 is sandwiched between the flange portion 68 of the oil separation pipe 280 and the flange portion 284 of the fitting cylinder 282 fitted to the cylinder portion 66, and the oil separation pipe 280 is connected to the gasket. 38 can be held securely. That is, the displacement of the oil separation pipe 280 toward the rear housing 14 is restricted under the engagement action of the flange portion 68 with the gasket 38, and the engagement with the gasket 38 by the flange portion 284 of the fitting cylinder 282. Under the combined action, displacement of the cylindrical portion 66 toward the fixed scroll 22 is restricted.

  As a means for fitting the fitting cylindrical body 282 to the cylindrical portion 66, the fitting cylindrical body 282 may be integrally crimped radially inward after the fitting cylindrical body 282 is inserted into the cylindrical portion 66. The inner peripheral diameter of the cylindrical body 282 may be set smaller than the outer peripheral diameter of the cylindrical portion 66, and the fitting cylindrical body 282 may be press-fitted into the cylindrical portion 66. Further, the fitting cylinder 282 is formed of an elastic body having a resilient force directed inward in the radial direction, and an engagement portion (for example, an uneven portion or a claw portion) is formed between the fitting cylinder 282 and the tube portion 66. And the fitting cylindrical body 282 may be engaged with the cylindrical portion 66 by the elastic force. Note that the joining method by fitting the oil separation pipe 280 and the fitting cylinder 282 includes the above-described caulking, press-fitting, snap fixing between the fitting cylinder 282 made of an elastic body and the engaging portion, and the like. You may make it carry out by, and you may make it carry out combining two or more.

  Furthermore, it is possible to improve the strength of the oil separation pipe 280 by configuring the oil separation pipe, which has conventionally been constituted of a single member, with two parts, the fitting cylinder 282 and the oil separation pipe 280. It becomes. Specifically, the strength in the vicinity of the root portion of the cylindrical portion 66 to which the fitting cylindrical body 282 is fitted can be improved. In other words, when the strength is set to be equivalent to that of a conventional single oil separation tube, the strength of each of the oil separation tube 280 and the fitting cylinder 282 can be set low. Therefore, for example, the oil separation pipe 280 and the fitting cylinder 282 can be easily formed from a thin plate-shaped press material, and the cost required for the oil separation pipe 280 can be reduced.

  Furthermore, the separation opening 202 of the gasket 38 through which the cylindrical portion 66 is inserted is preferably closed by sandwiching the gasket 38 by the flange portion 68 of the oil separation pipe 280 and the flange portion 284 of the fitting cylindrical body 282. Can do.

  Furthermore, a stepped portion 286 having a diameter larger than that of the tubular portion 66 is provided at a joint portion between the tubular portion 66 and the flange portion 68, and the diameter of the stepped portion 286 is set to the inner peripheral diameter of the separation opening 202 of the gasket 38. Since the displacement of the fitting cylinder 282 is restricted by the stepped part 286 when the fitting cylinder 282 is inserted into the cylinder 66, the cylinder 66 The fitting cylinder 282 can be reliably positioned with respect to the gap, and the gap for sandwiching the gasket 38 between the flange portion 68 and the fitting cylinder 282 can always be managed to be substantially constant.

  On the other hand, opposite to the oil separation pipe 280 according to the fourth modified example, a flange 294 is provided with respect to the separation opening 202 of the gasket 38 as in an oil separation pipe (oil separation member) 290 shown in FIG. The fitting cylinder (first fitting part) 292 is inserted, the cylinder part 66 of the oil separation pipe 290 is inserted from the fixed scroll 22 side to the outer peripheral side of the fitting cylinder 292, and the cylinder part 66 is inserted into the fitting cylinder. The body 292 may be fitted. As a result, the oil separation pipe 290 is reliably held against the gasket 38 sandwiched between the flange portion 294 and the flange portion 296 of the fitting cylinder 292 fitted to the cylinder portion 66.

  Finally, in the oil separation pipe (oil separation member) 300 according to the fifth modification, as shown in FIG. 20, the cylindrical portion 66 is inserted from the fixed scroll 22 side into the separation opening 202 of the gasket 38, The flange portion 68 is engaged with the end surface of the gasket 38, and the ring body 302 is inserted into the tubular portion 66 from the rear housing 14 side and is fitted to the root portion of the tubular portion 66.

  By configuring in this way, the oil separation pipe 300 is securely held against the gasket 38 because the gasket 38 is sandwiched between the flange portion 68 and the ring body 302. The ring body 302 may be caulked in the radially inward direction with respect to the cylindrical portion 66, may be press-fitted into the cylindrical portion 66, or the ring body 302 may be It may be formed of an elastic body (for example, a snap ring) and held by the cylindrical portion 66 by its elastic force.

  As a result, the ring body 302 is attached to the cylindrical portion 66 of the oil separation pipe 300, and the oil separation pipe 300 is reliably secured with a simple configuration in which the gasket 38 is sandwiched between the ring body 302 and the flange portion 68. Can be held in.

  Further, by sandwiching the gasket 38 between the flange portion 68 and the ring body 302, the separation opening 202 of the gasket 38 through which the tube portion 66 is inserted can be suitably closed.

  The above-mentioned joining means of the oil separation pipes 250, 270, 280, 290, 300 are integrally joined to the gasket 38, and when the gasket 38 is assembled between the fixed scroll 22 and the rear housing 14. The method is not particularly limited as long as it is prevented from falling off. Further, the bonding strength may be firmly bonded to the gasket 38, or may be bonded with a strength of a temporary fixing.

  Next, FIG. 21 shows a reciprocating compressor 350 that functions as a compressor according to the second embodiment.

  The reciprocating compressor 350 includes a rear housing (second housing) 352, a rear cylinder block 354 (hereinafter simply referred to as a rear block 354), a front cylinder block 356 (hereinafter simply referred to as a front block 356), and a front housing as casings. (Second housing) 358 is configured to be connected in this order from the left side in FIG. Valve plates (first housings) 360a and 360b are disposed between the rear housing 352 and the rear block 354 and between the front block 356 and the front housing 358, respectively.

  Sheet-like gaskets 362a to 362d are sandwiched between the rear housing 352, the rear block 354, the front block 356, the front housing 358, and the valve plates 360a and 360b, respectively.

  A plurality of cylinders 364 are formed in the rear block 354 and the front block 356 so as to be spaced apart from each other by a predetermined angle, and pistons 366 are disposed in the cylinders 364 so as to be displaceable along the axial direction. ing.

  At one end of the front housing 358, a hollow cylindrical portion 368 is formed in a substantially central portion, and an electromagnetic clutch 370 is rotatably fitted to the outer peripheral portion of the hollow cylindrical portion 368 via a bearing 372.

  The rear block 354 has an introduction port 374 and a lead-out port 376, and a discharge chamber 378 into which fluid compressed in the cylinder 364 is led inside the rear block 354 and the front block 356, respectively. In addition, a separation chamber 380 for separating the lubricating oil contained in the fluid introduced from the discharge chamber 378 and an oil storage chamber 382 for storing the lubricating oil separated in the separation chamber 380 are formed. The discharge chamber 378, the separation chamber 380, and the oil storage chamber 382 are independently formed through boundary walls (divided walls) 384a to 384c of the rear block 354 and the front block 356, and predetermined along the axial direction thereof. It is formed to be depressed at a depth.

  The discharge chamber 378 is provided so as to communicate with the cylinder 364 through the discharge ports 386 formed in the valve plates 360a and 360b, and is also communicated with the separation chamber 380 through a passage (not shown).

  The separation chamber 380 communicates with the lead-out port 376 via flow paths 388a and 388b formed inside the rear block 354 and the front block 356, and is substantially parallel to the axes of the rear block 354 and the front block 356. Are arranged substantially in line with the flow paths 388a and 388b. The separation chamber 380 is formed to be recessed with a substantially circular cross section so as to be separated from the valve plates 360a and 360b, and a part of an oil separation pipe (oil separation member) 390 is inserted into the separation chamber 380. Yes. Further, the gaskets 362a to 362d facing the separation chamber 380 are formed with a separation opening 392 that opens in substantially the same shape as the opening of the separation chamber 380, and a valve plate 360a facing the separation chamber 380. A communication hole 394 is formed in 360b. That is, the separation chamber 380 communicates with the flow paths 388a and 388b through the separation opening 392 and the communication hole 394.

  As shown in FIGS. 21 and 22, the oil separation pipe 390 includes a tubular tube portion (first fitting portion) 396 and a flange portion 398 having an enlarged diameter at an end portion of the tube portion 396. The cylindrical portion 396 is inserted toward the separation chamber 380 with respect to the separation openings 392 of the gaskets 362a and 362d, and the flange portion 398 is engaged with the circular recess 400 formed in the valve plates 360a and 360b. . The flange portion 398 is sandwiched between the rear housing 352 and the front housing 358 and the valve plates 360a and 360b via gaskets 362a and 362d, respectively. Further, a fitting cylinder (second fitting part) 402 having an inner diameter substantially equal to the outer diameter of the cylinder part 396 is inserted into the cylinder part 396 from the separation chamber 380 side, and the fitting cylinder is inserted. The body 402 and the cylindrical portion 396 are fitted.

  Further, since the separation chamber 380 communicates with the discharge chamber 378 from which fluid is discharged through a passage (not shown), the fluid in the discharge chamber 378 is introduced into the separation chamber 380 through the passage.

  That is, the separation chamber 380 communicates with the outlet port 376 via the flow paths 388 a and 388 b, and the fluid (refrigerant gas) introduced into the reciprocating compressor 350 from the introduction port 374 enters the cylinder 364. After being compressed by the piston 366, it is led out from the outlet port 376 through the discharge port 386 and the separation chamber 380.

  On the other hand, in the separation chamber 380, the fluid circulates between the separation chamber 380 and the cylindrical portion 396 of the oil separation pipe 390, and the lubricating oil contained in the fluid is generated by the swirling flow of the fluid. The fluid is centrifuged by the centrifugal force and separated to the inner peripheral surface side. Then, the lubricating oil flows to the oil storage chamber 382 through an oil passage 404 that communicates the separation chamber 380 and the oil storage chamber 382, and is stored in the oil storage chamber 382 by a predetermined amount.

  A rotation shaft 408 is inserted into the rear block 354, the front block 356, and the front housing 358 through a through hole 406 that penetrates along the axial direction. The through holes 406 are provided with radial bearings 410 that rotatably support the rotating shaft 408. The airtightness is maintained between the through hole 406 and the rotating shaft 408 in the front housing 358 by the seal member 412.

  The through-hole 406 of the front housing 358 communicates with the inside of the hollow cylindrical portion 368, and one end portion of the rotating shaft 408 is disposed so as to protrude from the hollow cylindrical portion 368. A bolt hole 414 is formed at one end of the protruding rotating shaft 408, and the rotating shaft 408 and the hub 418 constituting the electromagnetic clutch 370 are connected to each other by a bolt 416 screwed into the bolt hole 414. Yes.

  In addition, first to fourth disks 420a to 420d are fitted in a substantially central portion along the axial direction of the rotating shaft 408, and a first thrust is interposed between the first and second disks 420a and 420b. A bearing 422 is disposed, a swash plate 426 is disposed between the second and third disks 420b and 420c, and a second thrust bearing 424 is disposed between the third and fourth disks 420c and 420d. Is arranged. The first to fourth disks 420a to 420d, the first and second thrust bearings 422 and 424, and the swash plate 426 are fitted to the rotation shaft 408, respectively.

  The disk portion of the swash plate 426 extends into a cylinder 364 defined by a rear block 354, a front block 356, and valve plates 360a and 360b. A piston 366 is fitted to the disk portion via a hemispherical shoe 428 (described later), and the piston 366 moves in the axial direction in the cylinder 364 as the swash plate 426 rotates. Reciprocate along.

  The piston 366 is formed with an intake port 430 through which the fluid introduced from the introduction port 374 is supplied to the discharge port 386 side, and the end surface of the piston 366 has an intake air that can be opened and closed at the opening of the intake port 430. Each valve 432 is mounted. A rivet 434 is mounted at a substantially central portion of the piston 366 so as to protrude toward the valve plates 360 a and 360 b, and a stopper 436 is formed to protrude from the head of the rivet 434. Accordingly, when the intake valve 432 is opened, the intake valve 432 contacts the stopper portion 436.

  A pair of hemispherical shoes 428 is accommodated inside the piston 366 via a hemispherical groove 438, and the swash plate 426 is sandwiched by the set of hemispherical shoes 428, and the piston 366 is connected to the swash plate 426. Are fitted.

  The rear block 354, the rear housing 352, the front block 364, and the front block 356 are provided with pin holes 442 for inserting the pins 440. By inserting the pins 440 into the pin holes 442, the rear block 354, The rear housing 352, the rear housing 358, and the front block 356 are positioned relative to each other.

  A discharge valve (not shown) is provided at the opening of the discharge port 386 so as to be openable and closable, and a valve stopper 444 is disposed outside the discharge valve.

  The electromagnetic clutch 370 fitted to the hollow cylindrical portion 368 in the front housing 358 has a function of rotating or stopping the rotation of the rotating shaft 408.

  The electromagnetic clutch 370 includes a hub 418, a clutch plate 446 connected to the hub 418 via a bolt 416, a rotor 448, and a coil 450 accommodated in the rotor 448. Further, a rotating shaft 408 is connected to the hub 418 via a bolt 416.

  As described above, in the reciprocating compressor 350 according to the second embodiment, the gasket is formed by the flange portion 398 of the oil separation pipe 390 and the flange portion 452 of the fitting cylindrical body 402 fitted to the cylindrical portion 396. The oil separation pipe 390 can be securely held with respect to the gaskets 362a and 362d by sandwiching 362a and 362d. Accordingly, the displacement of the oil separation pipe 390 toward the rear housing 352 and the front housing 358 is restricted under the engagement action of the flange portion 398 with respect to the gaskets 362a and 362d, and the flange portion of the fitting cylindrical body 402 Under the action of engagement with the gaskets 362a and 362d by 452, the displacement of the cylindrical portion 396 toward the valve plates 360a and 360b is restricted.

  As a means for fitting the fitting cylindrical body 402 to the cylindrical portion 396, the fitting cylindrical body 402 may be integrally crimped radially inward after the fitting cylindrical body 402 is inserted into the cylindrical portion 396. The inner peripheral diameter of the cylindrical body 402 may be set smaller than the outer peripheral diameter of the cylindrical portion 396, and the fitting cylindrical body 402 may be press-fitted into the cylindrical portion 396.

  Furthermore, it is possible to improve the strength of the oil separation pipe 390 by configuring the oil separation pipe, which has conventionally been formed of a single member, with two parts, the fitting cylinder 402 and the oil separation pipe 390. It becomes. Specifically, the strength in the vicinity of the root portion of the cylindrical portion 396 to which the fitting cylindrical body 402 is fitted can be improved. In other words, when the strength is set to be equivalent to that of the conventional single oil separation tube 390, the strength of each of the oil separation tube 390 and the fitting cylinder 402 can be set low. Therefore, for example, the oil separation pipe 390 and the fitting cylinder 402 can be easily formed from a thin plate-shaped press material, and the cost required for the oil separation pipe 390 can be reduced.

  The reciprocating compressor 350 according to the second embodiment described above is not limited to the case where the oil separation pipe 390 is applied, but the scroll compressor according to the first embodiment. 10, any one of the oil separation pipes 250, 260, 270, 280, 290, 300 of the first to fifth modifications may be applied.

1 is an overall longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention. FIG. 2 is a partially omitted exploded perspective view of the scroll compressor of FIG. 1. It is the top view which looked at the fixed scroll in the scroll compressor of Drawing 2 from the fixed side spiral wall side. It is a longitudinal cross-sectional view which shows the movable scroll, fixed scroll, gasket, and rear housing in the scroll compressor of FIG. FIG. 2 is an exploded perspective view in which the fixed scroll and the rear housing of FIG. 1 are developed in a direction in which they are separated from each other with the joint surface as a boundary. It is the top view seen from the back side to which the gasket in a fixed scroll is mounted | worn. FIG. 7 is an exploded perspective view showing a state where an oil separation pipe is detached from the back surface of the fixed scroll of FIG. 6. It is a longitudinal cross-sectional view which shows the state which attached the oil separation pipe | tube to the circular recessed part of the fixed scroll, and was clamped between the said fixed scroll and the rear housing via the gasket. It is a longitudinal cross-sectional view which shows the state by which the oil separation pipe which concerns on the modification was fixed to the fixed scroll via the fixing bolt. It is a top view of the rear housing seen from the joint surface side where a gasket is mounted | worn. It is a top view which shows the state which mounted | wore with the gasket with respect to the joint surface of the rear housing, and overlapped the 1st-4th recessed part and the lead-out hole of the fixed scroll. It is a longitudinal cross-sectional view which shows the relationship between the separation chamber, the lead-out passage, and the throttle hole of the gasket in a state where the fixed scroll, the gasket and the rear housing are assembled. It is sectional drawing along the XIII-XIII line | wire of FIG. It is the top view which looked at the gasket from the fixed scroll side. It is an expanded longitudinal cross-sectional view which shows the state with which the oil separation pipe concerning the 1st modification was mounted | worn between a gasket and the rear housing. FIG. 6 is an enlarged vertical cross-sectional view showing a state where an oil separation pipe according to a second modification integrally formed with a gasket is mounted between a fixed scroll and a rear housing. It is an expanded longitudinal cross-sectional view which shows the state with which the oil separation pipe | tube which concerns on the 3rd modification inserted lightly with respect to the isolation | separation opening part of the gasket was mounted | worn between the fixed scroll and the rear housing. It is an expanded longitudinal cross-sectional view which shows the state with which the oil separation pipe which concerns on a 4th modification was mounted | worn with respect to the isolation | separation opening part of a gasket. Opposite to the oil separation pipe in FIG. 18, an enlarged vertical section showing a case where the fitting cylinder is attached to the gasket from the fixed scroll side, and the oil separation pipe is attached to the fitting cylinder from the rear housing side. FIG. It is an expanded longitudinal cross-sectional view which shows the state with which the oil separation pipe which concerns on a 5th modification was mounted | worn with the separation opening part of the gasket via the ring body. It is a whole longitudinal cross-sectional view of the reciprocating compressor which concerns on the 2nd Embodiment of this invention. FIG. 22 is an enlarged longitudinal sectional view in the vicinity of an oil separation pipe and a separation chamber in FIG. 21.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Scroll type compressor 12, 358 ... Front housing 14, 352 ... Rear housing 16 ... Inlet port 18, 386 ... Discharge port 22 ... Fixed scroll 22a ... Back surface 24 ... Movable scroll 26 ... Fixed side board | substrate part 28 ... Fixed side spiral Wall 30 ... Guide passage 32 ... Oil supply hole 34 ... Supply passage 36 ... Damping walls 38, 262, 362a to 362d ... Gaskets 40, 378, 386 ... Discharge chamber 42 ... Lead-out hole 44 ... Discharge valves 52, 52a, 250, 260 270, 280, 290, 300, 390 ... oil separation pipes 60, 252, 400 ... circular recess 62, 380 ... separation chamber 64 ... discharge chamber 66, 272, 396 ... cylindrical portion 68, 296, 398 ... flange portion 80, 382 ... Oil storage chamber 86 ... Filter 88 ... Filter chamber 90 ... Oil supply groove 106 ... Movable substrate part 108 ... Movable spiral wall DESCRIPTION OF SYMBOLS 10 ... Compression chamber 116 ... Rotating shaft 160, 370 ... Electromagnetic clutch 172 ... Joint surface 186 ... Derivation passage 202, 392 ... Separation opening 212 ... Restriction hole 214 ... Bead 282,292, 402 ... Fit cylinder 284,294, 452 ... collar 302 ... ring body 350 ... reciprocating compressor 360a, 360b ... valve plate 364 ... cylinder 366 ... piston 388a, 388b ... flow path 404 ... oil passage 426 ... swash plate 432 ... intake valve

Claims (5)

A first housing and a second housing joined to the first housing via a gasket; a discharge chamber into which the compressed fluid is led out in the second housing; and a fluid communicating with the discharge chamber In a compressor comprising a separation chamber that separates the lubricating oil contained therein, and an oil storage chamber that communicates with the separation chamber and stores the lubricating oil.
A dividing wall formed in the second housing and extending along an axial direction of the second housing to divide the discharge chamber and the separation chamber, respectively;
An oil separation member having a pipe portion inserted into the separation chamber and a flange portion formed at an end of the pipe portion, and distributing the fluid and lubricating oil in the separation chamber;
A gasket having a sealing portion for sealing the separation chamber;
With
The compressor characterized in that the oil separation member is integrally held by the gasket via the flange portion. The compressor according to claim 1, wherein
The oil separation member includes first and second fitting portions that are provided to face each other with the gasket interposed therebetween, and the first fitting portion and the second fitting portion are fitted to sandwich the gasket. A compressor characterized in that it is held. The compressor according to claim 2, wherein
The first and second fitting portions are each formed in a cylindrical shape having a flange portion having an enlarged diameter, and the first fitting portion is formed with a smaller diameter than the second fitting portion, and the first fitting portion The compressor is characterized in that the second fitting portion is fitted to the outer peripheral side of the first gasket and the gasket is sandwiched between flange portions of the first and second fitting portions. In the compressor given in any 1 paragraph of Claims 1-3,
The compressor has a movable scroll and a fixed scroll that functions as the first housing, and is a scroll type compressor that compresses fluid under a turning action of the movable scroll with respect to the fixed scroll. Machine. In the compressor given in any 1 paragraph of Claims 1-3,
The compressor includes a valve plate that functions as the first housing, a piston that is displaceable along an axial direction, and a swash plate that is fitted to be inclined with respect to the axis of the piston, A compressor characterized by being a reciprocating compressor that compresses a fluid by displacing the piston under the rotational action of a swash plate.

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