JP4156392B2 - Swing swash plate type variable capacity compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a swing swash plate type variable capacity compressor suitable for application to refrigerant compression, such as a vehicle refrigeration cycle apparatus.
[0002]
[Prior art]
As conventional swing swash plate type variable displacement compressors, for example, those shown in Patent Document 1 and Patent Document 2 are known. This swing swash plate type variable capacity compressor is connected to a piston that compresses refrigerant and is housed in a crank chamber (swash plate chamber), and swings through a swing swash plate that can swing with a variable tilt angle, and a pressure control valve. A control refrigerant supply passage for guiding the high-pressure gas in the discharge chamber into the crank chamber, and a suction communication passage for discharging the gas in the crank chamber to the low-pressure suction chamber.
[0003]
The pressure in the crank chamber is determined by the balance between the amount of high-pressure gas introduced into the crank chamber and the amount of gas exhausted from the crank chamber, and the pressure in the crank chamber is increased or decreased by a pressure control valve. By changing the back pressure to be applied, the inclination angle of the swing swash plate is changed to realize variable discharge capacity.
[0004]
More specifically, for example, when the discharge capacity is reduced due to excessive cooling capacity or the like, the inclination angle of the swing swash plate is reduced by increasing the pressure in the crank chamber by introducing high-pressure control refrigerant into the crank chamber. This reduces the compression stroke of the piston. Conversely, when the discharge capacity is increased, the refrigerant in the crank chamber is released to the suction side and the pressure in the crank chamber is decreased, so that the inclination angle of the swing swash plate is increased and the compression stroke of the piston is increased.
[0005]
Further, these swing swash plate type variable capacity compressors generally have a rotation prevention mechanism that prevents the swing swash plate from rotating, a swing support mechanism that supports the swing of the swing swash plate, and the like. Is arranged.
[0006]
[Patent Document 1]
Japanese Patent Application Laid-Open No. 01-45978
[Patent Document 2]
Japanese Patent Laid-Open No. 04-159463
[Problems to be solved by the invention]
However, in the above-described prior art, like the fixed capacity swing swash plate compressor, the intake refrigerant is always guided to the crank chamber, and the anti-rotation mechanism and the swing support mechanism disposed in the crank chamber with the intake refrigerant. It cannot be lubricated. As a result, particularly when the rotation speed is excessive and the cooling capacity is excessive and the small capacity operation is performed, the non-rotating mechanism and the swing support mechanism are not sufficiently lubricated, which may cause problems such as seizure.
[0009]
The present invention has been made in view of the above-mentioned problems of the prior art, and its purpose is to improve the lubricity of the anti-rotation mechanism of the swing swash plate and the swing support mechanism, and to prevent the high sliding conditions. An object of the present invention is to provide a swing swash plate type variable capacity compressor that is excellent in reliability even when rotating and having a small capacity.
[0010]
[Means for Solving the Problems]
The present invention, in order to achieve the above object, employing the technical means described below. That is, according to the first aspect of the present invention, the housing (110, 120) in which the rotating shaft (150) is housed and the cylinder bore (123) that houses the reciprocating piston (220 ) is formed, and the shaft ( 150) and a swiveling member (180) having an inclined surface inclined with respect to the shaft (150) and housed in the crank chamber (121) via the inclined surface and the thrust bearing (183). The pivot member (200) that reciprocates the piston (220) by swinging the pivot member (180) with a variable tilt angle as the swivel member (180) rotates, and a center hole formed in the housing (110, 120). 124) via a detent mechanism (125, 191c), a support member (191) disposed so as to be slidable in the axial direction, and a support member (19 ) End the joint (192, 193) from the composed swing support mechanism (190) for swingably supporting the swing member (200) to the pressure control valve from the discharge chamber (132) and (230) And a control refrigerant supply path (126) for guiding the control refrigerant into the crank chamber (121) via the pressure control valve (230) to adjust the pressure in the crank chamber (121), and the swing member (200) In the swing swash plate type variable capacity compressor that changes the discharge capacity by changing the inclination angle of
The control refrigerant supply path (126) includes a part of the inner space of the center hole (124) and a passage formed in the support member (191), and is provided with a detent mechanism (125, 191c ). The control refrigerant is ejected to the joints (192, 193) .
[0011]
This is because the present invention pays attention to the fact that the control refrigerant is actively used for lubrication, so that mist-like oil can be supplied to the anti-rotation mechanism (125, 191c ) together with the control refrigerant. And lubricity is improved. Moreover, since the capacity becomes smaller in the high rotation range where the sliding conditions are severe, the amount of control refrigerant increases, and the amount of mist-like oil supplied to the anti- rotation mechanism (125, 191c ) and the joints (192, 193) also increases. It is possible to provide a swing swash plate type variable displacement compressor that is increased in reliability and excellent in reliability.
[0012]
In the second aspect of the present invention, the anti-rotation mechanism (125, 191c) is disposed at the center of the plurality of cylinder bores (123), and the support member (190) of the swing support mechanism (190) that supports the swing member (200) ( 191) is provided with a third control refrigerant supply path (126c) and a jet outlet (126d) as a part of the control refrigerant supply path (126).
[0013]
This simplifies the routing of the control refrigerant supply path (126). Further, by supplying mist-like oil together with the control refrigerant to the anti-rotation mechanism (125, 191c) to improve lubricity, and ejecting the control refrigerant in the vicinity of the swing support mechanism (190), the swing support mechanism Also in (190), lubricity is improved by supplying mist-like oil together with the control refrigerant. In addition, since the capacity becomes smaller in the high rotation range where the sliding conditions are severe, the amount of the control refrigerant increases, and the amount of mist-like oil supplied to the anti-rotation mechanism (125, 191c) and the swing support mechanism 190 also increases. The swing swash plate type variable capacity compressor can be more reliable.
[0014]
The invention according to claim 3 is characterized in that the jet outlet (126d) is branched in the direction of the sliding sliding portions (190a to 190d) of the swing support mechanism (190). As a result, the control refrigerant is ejected toward the sliding sliding portions (190a to 190d), and the sliding slopes that improve the lubricity of the sliding sliding portions (190a to 190d) more reliably and have excellent reliability. It can be set as a plate-type variable capacity compressor.
[0015]
In the invention described in claim 4, the suction port of the suction communication passage for introducing the control refrigerant in the crank chamber (121) the suction chamber (131) (122) and (122a), exposed internal side of the shaft seal (160) It is characterized by opening in the open space . The control refrigerant blown into the crank chamber (121) is recovered from the suction port (122a) opened in the space where the inner side surface of the shaft seal (160) is exposed , and thus the shaft seal Also in (160), mist-like oil is supplied together with the control refrigerant so that the lubricity is improved and the swing swash plate type variable capacity compressor can be made more reliable.
[0016]
In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIGS. 1-6 shows 1st Embodiment of this invention, FIG. 1 is sectional drawing which shows the rocking | fluctuation swash plate type | mold variable capacity compressor in 1st Embodiment. First, a specific configuration will be described mainly with reference to FIG.
[0018]
A swing swash plate type variable capacity compressor (hereinafter referred to as a compressor) 100 is disposed, for example, in a refrigeration cycle apparatus for a vehicle and operates by receiving driving force of a vehicle engine (hereinafter referred to as an engine). The refrigerant inside is compressed to a high temperature and a high pressure. A swing swash plate (swing member) 200 that can change the discharge capacity per rotation is cantilevered by a swing support mechanism 190 that forms a joint here.
[0019]
A middle housing 120 is joined to the rear end side of the front housing 110, and a rear housing 130 is joined to the rear end side via a valve plate 140, which are joined by a through bolt (not shown). The front housing 110 is sealed by a shaft seal 160 and accommodates a shaft 150. The shaft 150 is rotatably supported by a bearing 170 fixed to the front housing 110.
[0020]
An arm 151 is integrally formed on the rear end side of the shaft 150. Note that a pulley (not shown) is attached to the distal end side of the shaft 150, and the driving force of the engine is transmitted to the shaft 150 via the belt hung on the pulley to rotate. A plurality of cylinder bores 123 are formed in the middle housing 120 so as to surround the central axis of the shaft 150, and pistons 220 are fitted in the cylinder bores 123 so as to be able to reciprocate.
[0021]
The crank chamber (swash plate chamber) 121 is an internal space formed by the front housing 110 and the middle housing 120. A swing swash plate 200 that is swingably supported by a swing support mechanism 190 is accommodated in the crank chamber 121, and the swing swash plate 200 is connected to each piston 220 via a rod 210.
[0022]
2 to 5 show the detailed structure of the swing support mechanism 190, FIG. 2 is a cross section taken along the line AA in FIG. 1, FIG. 3 is a cross section taken along the line BB in FIG. FIG. 5 shows a cross section taken along the line DD in FIG. The swing support mechanism 190 forms a so-called universal joint (here, an inconstant velocity universal joint), and a first rotating member 192 is connected to a tip portion of a center shaft (support member) 191 by a first pin member 193. Further, the first rotating member 192 and the second rotating member 194 are connected by the second pin member 195.
[0023]
The first pin member 193 and the second pin member 195 are arranged so that their axial centers intersect with each other, and the second rotating member 194 can swing in any direction with respect to the center shaft 191. Yes. Therefore, the swing swash plate 200 fixed to the second rotating member 194 can be inclined at an arbitrary angle (inclination angle θ) with respect to the plane orthogonal to the center shaft 191. Specifically, the swing swash plate 200 has a maximum tilt position as shown in FIG. 1 from a position close to perpendicular to the axis of the center shaft 191 (a state in which the tilt angle θ is almost zero and close to FIG. 6). It can be tilted up to.
[0024]
Here, a torque that rotates the swing swash plate 200 by a force due to the pressure of the refrigerant and a force due to the inertia of the swing swash plate 200, the rod 210, and the piston 220 acts on the anti-rotation mechanism. Therefore, the contact surface 190a between the center shaft 191 and the first rotating member 192 and the contact surface 190b between the first pin member 193 and the first rotating member 192 slide and slide while receiving the torque. Similarly, the contact surface 190c of the first rotating member 192 and the second rotating member 194 and the contact surface 190d of the second pin member 195 and the first rotating member 192 slide and slide while receiving the torque.
[0025]
The support portion 191a on the rear end side of the center shaft 191 is inserted into a center hole 124 provided in the center portion of the middle housing 120 (on the center axis of the shaft 150). Spline protrusions 191c and spline grooves 125 are formed on the outer periphery of the support portion 191a and the inner periphery of the center hole 124, respectively, and the center shaft 191 can slide in the axial direction of the center hole 124. And rotation in the circumferential direction is prevented. A coil spring 196 is interposed between the support portion 191a and the valve plate 140, and the center shaft 191 is biased toward the shaft 150 side.
[0026]
A swiveling member 180 is mounted on the surface of the swash plate 200 on the shaft 150 side via a thrust bearing 183 so as to be rotatable in the circumferential direction of the swing swash plate 200. A projecting portion 181 is provided on the shaft 150 side of the turning member 180 and is connected by a connecting pin 152 through a long hole 182 formed in the arm 151 so as to form a hinge mechanism with the arm 151 of the shaft 150. As the connecting pin 152 rotates and slides with respect to the long hole 182, the inclination angle θ of the swash plate 200 changes.
[0027]
The rear housing 130 is partitioned into a suction chamber 131 and a discharge chamber 132. A suction hole 142 and a discharge hole 143 are formed in the valve plate 140 corresponding to each cylinder bore 123, and a working chamber V formed between the valve plate 140 and each piston 220 is formed in the suction hole 142 and the discharge hole. The suction chamber 131 and the discharge chamber 132 are communicated with each other through a hole 143.
[0028]
Each suction hole 142 is provided with a suction valve 145 that opens and closes the suction hole 142 according to the reciprocating motion of each piston 220, and each discharge hole 143 has a discharge hole 143 according to the reciprocating motion of each piston 220. A discharge valve 146 that opens and closes while being regulated by the valve stop plate 147 is provided.
[0029]
The rear housing 130 is provided with a suction port (not shown) so that the suction chamber 131 and the evaporator of the refrigeration cycle apparatus are connected. Similarly, the rear housing 130 is provided with a discharge port (not shown) so that the discharge chamber 132 and the condenser of the refrigeration cycle apparatus are connected.
[0030]
The rear housing 130 is provided with a pressure control valve 230 for adjusting the pressure in the crank chamber 121. A current is supplied to a coil (not shown) in the pressure control valve 230 to slide in the longitudinal direction (perpendicular to the paper surface of FIG. 1), and the discharge chamber 132 and the crank chamber 121 are communicated with each other. A rod 231 is provided as a control valve body that opens and closes the refrigerant supply path 126. Incidentally, the rod 231 operates to close the control refrigerant supply path 126 as the current supplied to the coil increases.
[0031]
As a feature of the present invention, the control refrigerant supply path 126 is connected to the first control refrigerant supply path 126a connected from the discharge chamber 132 to the rod 231 and the center hole 124 into which the center shaft 191 is inserted from the rod 231. The second control refrigerant supply path 126b, and the third control refrigerant supply path 126c provided in the center hole 124 and in the center shaft 191 inserted therein. The control refrigerant is ejected to the top.
[0032]
Further, 190a to 190d shown in FIG. 2 are sliding sliding portions in the swing support mechanism 190. As shown in FIG. 5, the jet outlet 126d at the tip of the third control refrigerant supply path 126c It branches off in the direction of each sliding sliding part 190a-190d of the dynamic support mechanism 190. The middle housing 120 is provided with a suction communication passage 122 that discharges the control refrigerant introduced into the crank chamber 121 to the suction chamber 131.
[0033]
Next, the operation and effect of the compressor 100 based on the above configuration will be described. In operation of the compressor 100, when the shaft 150 rotates by receiving the driving force of the engine, the turning member 180 rotates and swings. Only the swing motion of the swivel member 180 is transmitted to the swing swash plate 200, and the coupled piston 220 reciprocates in the cylinder bore 123 to compress the refrigerant sucked from the suction chamber 131 and from the discharge chamber 132. Discharge.
[0034]
The variable discharge capacity of the compressor 100 will be described. When the heat load of the refrigeration cycle apparatus is high, the current supplied to the coil of the pressure control valve 230 is increased. Then, the rod 231 slides to the side closing the control refrigerant supply path 126 by the magnetic force of the coil. When the control refrigerant supply path 126 is blocked, the degree of communication between the discharge chamber 132 and the crank chamber 121 decreases, and the amount of control refrigerant gas supplied from the discharge chamber 132 to the crank chamber 121 decreases.
[0035]
Further, the control refrigerant gas escapes from the crank chamber 121 to the suction chamber 131 via the suction communication passage 122, whereby the pressure in the crank chamber 121 decreases. Therefore, the balance between the pressure in the cylinder bore 123 and the crank chamber 121 is changed to the side where the inclination angle θ of the swing swash plate 200 is large (the state shown in FIG. 1), and the stroke of the piston 220 is increased to increase the discharge capacity. .
[0036]
On the other hand, when the heat load of the refrigeration cycle apparatus is low, the current supplied to the coil of the pressure control valve 230 is reduced. Then, the rod 231 slides to the side that opens the control refrigerant supply path 126 by the magnetic force of the coil. When the control refrigerant supply path 126 is opened, the degree of communication between the discharge chamber 132 and the crank chamber 121 increases, the amount of control refrigerant gas supplied from the discharge chamber 132 to the crank chamber 121 increases, and the pressure in the crank chamber 121 increases. Increase.
[0037]
Therefore, the inclination angle θ of the swing swash plate 200 is varied to the smaller side (state shown in FIG. 6) from the balance of the pressure in the cylinder bore 123 and the crank chamber 121, and the stroke of the piston 220 is reduced to reduce the discharge capacity. .
[0038]
Next, features in this embodiment will be described. First, a control refrigerant supply passage 126 is provided in or near the spline uneven grooves 125 and 191c (rotation prevention mechanism) for preventing the rotation of the swing swash plate 200, and the control refrigerant is jetted into the spline uneven grooves 125 and 191c. ing.
[0039]
This is because the present invention pays attention to the fact that the control refrigerant is actively used for lubrication, so that mist-like oil can be supplied to the spline uneven grooves 125 and 191c together with the control refrigerant. Improves. In addition, since the volume is smaller in the high rotation range where the sliding conditions are severe, the amount of control refrigerant increases, the amount of mist-like oil supplied to the spline uneven grooves 125 and 191c also increases, and the rocking swash plate has excellent reliability. Type variable capacity compressor.
[0040]
Spline uneven grooves 125 and 191c (anti-rotation mechanism) are arranged at the center of the plurality of cylinder bores 123, and a part of the control refrigerant supply path 126 is connected to the center shaft 191 of the swing support mechanism 190 that supports the swing swash plate 200. A third control refrigerant supply passage 126c and an outlet 126d thereof are provided.
[0041]
Thereby, the routing route of the control refrigerant supply passage 126 is simplified. Further, mist-like oil is supplied to the spline uneven grooves 125 and 191c together with the control refrigerant to improve the lubricity, and the control refrigerant is blown out in the vicinity of the swing support mechanism 190 so that the control is also performed in the swing support mechanism 190. Mist oil is supplied together with the refrigerant to improve lubricity. In addition, since the capacity becomes smaller in the high rotation range where the sliding conditions are severe, the amount of control refrigerant increases, and the amount of mist-like oil supplied to the spline uneven grooves 125 and 191c and the swing support mechanism 190 also increases, making it more reliable. The swash plate type variable capacity compressor can be made excellent in performance.
[0042]
Further, as shown in FIG. 5, the jet outlet 126d has four holes formed toward the outer periphery so as to jet the control refrigerant to the four sliding parts of the swing support mechanism 190. Therefore, it is possible to more reliably supply the mist-like oil together with the control refrigerant to the four sliding parts, thereby improving the lubricity and providing a highly reliable swing swash plate type variable capacity compressor. be able to.
[0043]
(Second Embodiment)
FIG. 7 is a cross-sectional view showing a swing swash plate type variable capacity compressor in a second embodiment of the present invention. The first embodiment is different from the first embodiment only in the route of the suction communication passage 122 that discharges the control refrigerant introduced into the crank chamber 121 to the suction chamber 131. Specifically, as shown in FIG. 7, the position of the suction communication passage 122 for guiding the control refrigerant in the crank chamber 121 to the suction chamber 131 is changed and provided in the front housing 110 and the middle housing 120, and the suction port 122a is connected to the shaft. Opening in the vicinity of the seal 160.
[0044]
The control refrigerant ejected into the crank chamber 121 is recovered from the suction port 122a that opens near the shaft seal 160, whereby mist-like oil is supplied to the shaft seal 160 together with the control refrigerant. The swash plate type variable capacity compressor with improved lubricity and superior reliability can be obtained.
[0045]
( Reference example )
FIG. 8 is a cross-sectional view showing a swing swash plate type variable displacement compressor in a reference example of the present invention. The anti-rotation mechanism of the swing swash plate 200 and the control refrigerant supply path 126 are different from the first and second embodiments described above. Specifically, as shown in FIG. 8, a rotation prevention mechanism is provided on the outer peripheral portion of the swing swash plate 200. This anti-rotation mechanism is assembled with a beam-like portion 240 formed in the middle housing 120 and an outer peripheral portion of the swing swash plate 200 so as to be rotatable at one end and sandwiching the beam-like portion 240 at the other end. And a sliding member 250 that slides along.
[0046]
FIG. 9 shows an EE cross section in FIG. In this anti-rotation mechanism, both side end surfaces 241 of the beam-shaped portion 240 and the U-shaped portion 251 of the sliding member 250 slide while supporting the rotation torque acting on the swinging swash plate 200. The control refrigerant supply path 126 is formed on both sides so that the control refrigerant is supplied to both side end surfaces 241 of the beam-like portion 240.
[0047]
With the above configuration, as in the first embodiment, mist-like oil can be supplied to the beam-like portion 240 and the sliding member 250 together with the control refrigerant, and lubricity is improved. In addition, since the capacity becomes smaller in the high rotation range where the sliding conditions are severe, the amount of control refrigerant increases, the amount of mist-like oil supplied to the beam-like portion 240 and the sliding member 250 also increases, and the reliability is excellent. A swing swash plate type variable capacity compressor can be provided.
[0048]
FIG. 10 shows a variation of the above reference example (FIG. 9). The pair of control refrigerant supply paths 126 formed on both sides of the beam-shaped portion 240 in FIG. One control refrigerant supply path 126 that opens on both sides of the portion 240 may be used.
[0049]
(Other embodiments)
In the above-described embodiment, the swing support mechanism 190 using an inconstant velocity universal joint has been described. However, the present invention is not limited to this, and a constant velocity universal joint may be used. Also, as shown in FIG. 11, the tip 191b of the center shaft 191 may be a spherical sliding shoe.
[0050]
In this case, in order to prevent the swinging swash plate 200 from rotating together with the shaft 150, the rotation mechanism of the swinging swash plate 200 is provided in the guide groove 240 a provided in the front housing 110 as a detent mechanism. It may have a structure in which sliding pins 250a provided on the outer periphery are inserted and slid. Further, the connection between the swing swash plate 200 and the piston 220 is not limited to the rod 210, and a spherical sliding shoe may be used.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a swash plate type variable displacement compressor according to a first embodiment of the present invention.
2 shows an AA cross section in FIG.
FIG. 3 shows a BB cross section in FIG. 2;
4 shows a CC cross section in FIG. 2. FIG.
5 shows a DD cross section in FIG. 3. FIG.
6 is a cross-sectional view showing a state in which the discharge capacity is reduced in the compressor of FIG. 1. FIG.
FIG. 7 is a cross-sectional view showing a swing swash plate type variable displacement compressor in a second embodiment of the present invention.
8 is a cross-sectional view illustrating a swash plate type variable displacement compressor in a reference example of the present invention.
FIG. 9 shows an EE cross section in FIG.
FIG. 10 shows a variation of the reference example (FIG. 9) of the present invention.
FIG. 11 is a cross-sectional view showing a swing swash plate type variable displacement compressor according to another embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 100 Oscillating swash plate type variable capacity compressor 121 Crank chamber 122 Suction communication path 122a Suction port 123 Cylinder bore 125 Spline groove (non-rotating mechanism)
126 Control refrigerant supply path 126c Third control refrigerant supply path 126d Spout 131 131 Suction chamber 132 Discharge chamber 160 Shaft seal 190 Swing support mechanism 190a-190d Sliding part 191 Center shaft (support member)
191c Spline protrusion (anti-rotation mechanism)
200 Oscillating swash plate (oscillating member)
220 Piston 230 Pressure control valve

Claims (4)

A housing (110, 120) formed with a cylinder bore (123) for housing a rotating shaft (150) and a reciprocating piston (220) ;
A turning member (180) that rotates integrally with the shaft (150) and has an inclined surface inclined with respect to the shaft (150);
The piston (220) is reciprocated by being housed in a crank chamber (121), connected to the inclined surface through a thrust bearing (183), and swinging in a variable inclination angle with the rotation of the turning member (180). A rocking member (200) to be moved;
A support member (191) disposed in a center hole (124) formed in the housing (110, 120) via an anti-rotation mechanism (125, 191c) so as to be slidable in the axial direction; and the support member A swing support mechanism (190) including joints (192, 193) that swingably support one end of (191) on the swing member (200);
A control refrigerant supply path (126) for guiding the control refrigerant from the discharge chamber (132) to the crank chamber (121) through the pressure control valve (230),
In the swing swash plate type variable displacement compressor that adjusts the pressure in the crank chamber (121) by the pressure control valve (230) and changes the discharge angle by changing the inclination angle of the swing member (200),
Before SL control coolant supply passage (126) includes a portion of the interior space of the center hole (124) is constituted by a formed therein and passages of the support member (191), said detent mechanism ( 125, 191 c) and the joint (192, 193) , the control refrigerant is ejected to the swash plate type variable capacity compressor. The detent mechanism (125,191C) is disposed in the center of the plurality of the cylinder bores (123), wherein the support member (191) of said swing support mechanism for supporting the swing member (200) (190), The swing swash plate type variable according to claim 1, wherein a third control refrigerant supply path (126c) and an outlet (126d) thereof are provided as a part of the control refrigerant supply path (126). Capacity compressor.   The swing swash plate type variable according to claim 2, wherein the jet port (126d) is branched in the direction of each sliding sliding portion (190a to 190d) of the swing support mechanism (190). Capacity compressor. The suction port (122a) of the suction communication passage (122) for guiding the control refrigerant in the crank chamber (121) to the suction chamber (131) is opened in a space where the inner side surface of the shaft seal (160) is exposed. 4. The swing swash plate type variable displacement compressor according to claim 1, wherein the compressor is a swash plate type variable capacity compressor.

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