Variable displacement swash plate compressor

Abstract

The present invention provides a variable displacement swash plate type compressor, which smoothly supplies the oil contained in the refrigerant inside the crankcase to the drive shaft sealing area of ​​the front shell, and thus can reduce the frictional heat temperature between the drive shaft and the sealing component, prevent the leakage of refrigerant and pressure, and improve durability.

Description

Technical Field

[0001] The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor capable of smoothly supplying oil contained in a refrigerant in a crankcase to a sealing area of ​​a drive shaft of a front housing to reduce the temperature of frictional heat between the drive shaft and a sealing member, prevent leakage of refrigerant and pressure, and improve durability. Background Art

[0002] The compressor that constitutes a vehicle air conditioner is a device that selectively receives power from a power source through intermittent actuation of an electronic clutch, draws refrigerant gas from an evaporator into the interior, compresses the refrigerant gas through the linear reciprocating motion of a piston, and then discharges the refrigerant gas to a condenser. These compressors can be divided into various types based on compression methods and structures, and among these compressors, variable displacement compressors that can change the compression volume are also widely used.

[0003] Will refer to Figure 1 and Figure 2 A conventional variable displacement swash plate type compressor is described.

[0004] The variable displacement inclined plate type compressor may include: a cylinder block 10 having a plurality of cylinder bores 11 formed concentrically in an axial direction; a front housing 20 mounted on the front side of the cylinder block 10 and including a crankcase 21 formed in the front housing 20; a rear housing 30 mounted on the rear side of the cylinder block 10 and including a suction chamber 31 and a discharge chamber 32 formed in the rear housing 30; a plurality of pistons 40, each of which is inserted into the cylinder bores 11 of the cylinder block 10 for reciprocating motion and has a bridge portion 41 formed at the rear end portion of the piston 40; a drive shaft 50 having one end portion rotatably passing through the front housing 20 and a rear end portion inserted into the center of the cylinder block 10 to be rotatably mounted; and a rotor 60 disposed in the crankcase. 21 is internally connected to the drive shaft 50 so as to rotate together with the drive shaft 50; an inclined plate 70, which is rotatably mounted so that the sleeve 65 is slidably coupled to the outer periphery of the drive shaft 50, and the inclined plate 70 is fluidly connected to the hinge arm 61 of the rotor 60, so that when the inclined plate 70 rotates together with the rotor 60, the inclination angle of the inclined plate 70 relative to the drive shaft 50 is adjustable, and at the same time, the edge of the inclined plate 70 is rotatably coupled to the insertion space of the bridge portion 41 of the piston 40 via a base 45 provided in the insertion space; and a valve unit 80, which is mounted between the cylinder block 10 and the rear housing 30 to draw refrigerant from the suction chamber 31 into the cylinder bore 11 during the suction stroke, and to discharge the compressed refrigerant from the cylinder bore 11 to the discharge chamber 32 during the compression stroke.

[0005] A groove 62 may be formed in the hinge arm 61 of the rotor 60, and a connecting hinge arm 73 may be formed in the hub 71 of the swash plate 70 facing the hinge arm 61 of the rotor 60. The connecting hinge arm 73 protrudes from both sides of the hinge arm 61 and has a hinge pin 74 for fluidly coupling with the groove 62 of the hinge arm 61, connecting the hinge arm 73. In addition, the rotor 60 is rotatably supported by the thrust bearing 22 mounted on the inner wall surface of the front housing 20.

[0006] In this case, the inclination angle of the swash plate 70 with respect to the drive shaft 50 is adjusted by the control valve 90 installed in the rear housing 30 according to the pressure change in the crankcase 21 .

[0007] As described above, in a variable displacement swash plate type compressor, the plurality of pistons 40 concentrically arranged on the cylinder block 10 sequentially reciprocate due to the rotation of the swash plate 70, resulting in the suction, compression, and discharge of refrigerant. Furthermore, the inclination angle of the swash plate 70 is adjusted according to the pressure difference between the pressure in the crankcase 21 and the suction pressure in the cylinder bores 11, thereby varying the discharge capacity of the compressor.

[0008] On the other hand, the front housing 20 may be provided with a drive shaft sealing area 25 to seal between the front housing 20 and the drive shaft 50, thereby preventing leakage of refrigerant and pressure. The drive shaft sealing area 25 is provided with a sealing member 26 configured to seal between the front housing 20 and the drive shaft 50, and a radial bearing 27 installed on one side of the sealing member 26 to rotatably support the drive shaft 50.

[0009] In this case, the sealing member 26 is severely worn due to temperature increase of frictional heat caused by friction between the driving shaft 50 and the sealing member 26 during rotation of the driving shaft 50 in the case of long-term use, thereby causing leakage of refrigerant and pressure.

[0010] Therefore, in the prior art, the oil contained in the refrigerant in the crankcase 21 is supplied to the drive shaft sealing area 25 to reduce the temperature of the friction heat and form an oil film, thereby preventing leakage. Figure 2 As shown, an oil supply path 28 is formed in the front housing 20 , and oil that strikes the inner wall surface of the front housing 20 when the driving portion (rotor, swash plate, and drive shaft) rotates is supplied to the drive shaft seal area 25 .

[0011] However, the oil supply path 28 is almost closed by the thrust bearing 22 interposed between the inner wall surface of the front housing 20 and the rotor 60 , so that oil supply cannot be smoothly performed, thereby causing many problems in terms of lubricating the friction between the drive shaft 50 and the sealing member 26 .

[0012] As described above, if the oil supply is not smoothly performed, the temperature of the friction heat rises as described above, causing severe wear of the sealing member 26. Therefore, leakage of refrigerant and pressure is caused, resulting in many durability problems such as malfunction of the compressor. Summary of the Invention

[0013] Technical issues

[0014] An object of the present invention is to provide a variable displacement swash plate type compressor that can smoothly supply oil contained in the refrigerant in the crankcase to the sealing area of ​​the drive shaft of the front housing to reduce the temperature of frictional heat between the drive shaft and the sealing member, prevent leakage of refrigerant and pressure, and improve durability.

[0015] The technical problems to be solved by the present invention are not limited to the above technical problems, and those skilled in the art to which the present invention belongs can clearly understand other technical problems not mentioned above from the following description.

[0016] Technical Solution

[0017] 14. The axial displacement compressor of claim 13, wherein the plurality of oil supply holes are connected to each other via a plurality of channels, the plurality of channels being connected to each other via a plurality of channels. The plurality of oil supply holes are connected to each other via a plurality of channels. The plurality of oil supply holes are connected to each other via a plurality of channels. The plurality of oil supply holes are connected to each other via a plurality of channels.

[0018] In this manner, by covering the connecting groove with the seat ring to form the oil chamber communicating with the oil supply hole, the oil flowing through the groove can be smoothly supplied to the oil supply hole without flowing to another place.

[0019] According to an embodiment of the present invention, the seat ring may also cover at least a portion of the flow groove.

[0020] According to an embodiment of the present invention, the seat ring may cover at least a portion of the oil supply hole.

[0021] According to an embodiment of the present invention, the at least one or more oil supply holes may be formed in the connecting groove.

[0022] According to an embodiment of the present invention, the plurality of flow grooves may be radially formed in the inner wall surface of the front housing.

[0023] According to an embodiment of the present invention, the plurality of flow grooves may be formed in an upper portion of the front housing.

[0024] According to an embodiment of the present invention, the connection groove may be formed in the inner wall surface of the front housing in a circumferential direction around the insertion hole into which the drive shaft is inserted.

[0025] According to an embodiment of the present invention, the connection groove may be formed in the upper portion of the front housing such that both ends are blocked by the boundary portion to prevent the oil from flowing.

[0026] According to an embodiment of the present invention, the width of the connection groove may be formed to be greater than or equal to the diameter of the oil supply hole.

[0027] According to an embodiment of the present invention, the number of oil supply holes may be less than the number of flow grooves.

[0028] According to an embodiment of the present invention, the at least one or more oil supply holes may connect both ends of the connecting groove to the sealing area.

[0029] In this way, since the oil supply hole is connected to both ends of the connecting groove where oil flow is blocked by the boundary portion, oil flowing through the groove can be immediately supplied to the oil supply hole rather than being supplied to the oil supply hole after filling the oil chamber.

[0030] According to an embodiment of the present invention, the at least one or more oil supply holes may be formed radially outward from a boss portion protruding from an inner wall surface of the front housing.

[0031] According to an embodiment of the present invention, the variable displacement swash plate type compressor may further include a circulation groove formed in the inner wall surface of the front housing to circulate oil, and the circulation groove may be provided at an opposite side of the connection groove with respect to the boundary portion.

[0032] According to an embodiment of the present invention, the circulation groove may be formed in the inner wall surface of the front housing in a circumferential direction around the insertion hole into which the drive shaft is inserted.

[0033] According to an embodiment of the present invention, the variable displacement swash plate type compressor may further include an extension groove radially extending from the circulation groove.

[0034] In this way, the circulation groove and the extension groove are formed so that oil is supplied to the raceway and, at the same time, the oil is discharged back to the crankcase to achieve circulation.

[0035] According to an embodiment of the present invention, a radial bearing configured to rotatably support the drive shaft may also be installed in the sealing region.

[0036] According to an embodiment of the present invention, the variable displacement swash plate type compressor may further include an oil collecting portion connected to the flow groove radially outward from the flow groove and having a width narrowing toward the flow groove.

[0037] Beneficial effects

[0038] According to the present invention, by covering the flow groove, the connection groove, and the oil supply hole with the seat ring to form the oil chamber, the oil flowing through the groove can be smoothly supplied to the oil supply hole without flowing to another place.

[0039] In addition, since the oil supply hole is connected to both ends of the connecting groove where the oil flow is blocked by the boundary portion, the oil flowing through the groove can be immediately supplied to the oil supply hole rather than being supplied to the oil supply hole after the oil has been filled into the oil chamber.

[0040] Therefore, a large amount of oil is smoothly supplied to the sealing area of ​​the drive shaft of the front housing, making it possible to reduce the temperature of frictional heat between the drive shaft and the sealing member, thereby preventing leakage of refrigerant and pressure and improving durability.

[0041] In addition, by forming the circulation groove and the extension groove for circulating the oil, the oil can be supplied to the race, and at the same time, the oil can be discharged back to the crankcase, thereby enabling the oil to circulate.

[0042] In addition, since the number of oil supply holes is formed to be smaller than the number of flow grooves, machining time and cost can be reduced by forming fewer oil supply holes that require separate drilling machining.

[0043] The effects of the present invention are not limited to the above-described effects, and it should be understood that the effects of the present invention include all effects that can be derived from the detailed description of the present invention or the appended claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] Figure 1 is a cross-sectional view showing a conventional variable displacement swash plate type compressor.

[0045] Figure 2 is shown along Figure 1 A three-dimensional view of the front shell body taken in an oblique direction.

[0046] Figure 31 is a perspective view showing a state in which a front housing is vertically cut in a variable displacement swash plate type compressor according to an embodiment of the present invention.

[0047] Figure 4 It shows Figure 3 A perspective view of a front housing and components disposed in the front housing, wherein the components are separated;

[0048] Figure 5 It shows that Figure 4 A three-dimensional view of the front housing and the seat ring cut at a certain angle in the connected state.

[0049] Figure 6 yes Figure 4 Rear view of the front housing.

[0050] Figure 7 yes Figure 6 Stereoscopic image.

[0051] Figure 8 is a rear view showing a front housing separated from a variable displacement swash plate type compressor according to another embodiment of the present invention. DETAILED DESCRIPTION

[0052] Hereinafter, exemplary embodiments of a scroll compressor according to the present invention will be described with reference to the accompanying drawings.

[0053] In addition, the terms used below are defined in consideration of the functions in the present invention and may vary according to the intention of the user or operator or common practice. The following embodiments are not intended to limit the scope of protection of the present invention, but are merely exemplary constituent elements in the claims disclosed in the present invention.

[0054] In order to clearly describe the present invention, parts not related to the description will be omitted, and the same or similar constituent elements will be represented by the same reference numerals throughout the specification. Throughout the specification, unless otherwise expressly described, the word "include / comprise" and variations such as "including / comprising" or "having / containing" will be understood to imply the inclusion of the stated elements rather than the exclusion of any other elements.

[0055] First, refer to Figure 3 and Figure 4 A variable displacement swash plate type compressor according to an embodiment of the present invention will be described. In addition, the same reference numerals are assigned to the same parts as those in the prior art for description.

[0056] A variable displacement swash plate type compressor according to an embodiment of the present invention may include a cylinder block 10 in which a plurality of cylinder holes 11 are concentrically formed in an axial direction, and a front housing 20 defining a crankcase 21 in the cylinder block 10 may be installed on the front side of the cylinder block 10, and a rear housing 30 defining a suction chamber 31 and a discharge chamber 32 may be installed on the rear side of the cylinder block 10.

[0057] In each of the cylinder bores 11 of the cylinder block 10 , a plurality of pistons 40 , each having a bridge portion 41 formed at a rear end portion thereof, may be inserted and mounted to perform reciprocating motion.

[0058] In addition, a drive shaft 50 having one end portion rotatably passing through the front housing 20 and a rear end portion inserted into the center of the cylinder block 10 to be rotatably supported may be installed in the cylinder block 10. Here, the drive shaft 50 may be rotatably supported by the radial bearing 27.

[0059] In addition, a rotor 60 coupled to the drive shaft 50 to rotate together with the drive shaft 50 may be installed inside the crankcase 21. The rotor 60 may be rotatably supported by a thrust bearing member 100 installed on the inner wall surface of the front housing 20. Figure 4 As shown, the thrust bearing member 100 may include a pair of races 120a and 120b and a thrust bearing 140 disposed between the races 120a and 120b. The thrust bearing 140 may be implemented as a needle bearing including a plurality of radially arranged rollers.

[0060] In addition, the inclined plate 70 can be rotatably mounted on a sleeve 65 that is slidably connected to the drive shaft 50 inside the crankcase 21, and the inclined plate 70 can be fluidly connected to the hinge arm 61 of the rotor 60, so that when the inclined plate 70 rotates together with the rotor 60, the inclination angle of the inclined plate 70 relative to the drive shaft 50 is adjustable, and at the same time, the edge of the inclined plate 70 is rotatably connected to the insertion space of the bridge portion 41 of the piston 40 via the base 45 set in the insertion space.

[0061] A slot 62 may be formed in the hinge arm 61 of the rotor 60, and a connecting hinge arm 73 may be formed in the hub 71 of the swash plate 70 facing the hinge arm 61 of the rotor 60. The connecting hinge arm 73 protrudes from both sides of the hinge arm 61 and has a hinge pin 74 for fluidly coupling with the slot 62 of the hinge arm 61, connecting the hinge arms 73. Therefore, when the tilt angle of the swash plate 70 changes, the hinge pin 74 can support the tilting movement of the swash plate 70 while sliding along the slot 62.

[0062] At the same time, a valve unit 80 can be installed between the cylinder body 10 and the rear housing 30, which is used to suck refrigerant from the suction chamber 31 into the cylinder hole 11 during the suction stroke of the piston 40 and discharge the compressed refrigerant from the cylinder hole 11 to the discharge chamber 32 during the compression stroke of the piston 40.

[0063] In addition, a control valve 90 may be installed in the rear housing 30 to operatively connect the discharge chamber 32 and the crankcase 21 so that the inclination angle of the swash plate 70 is adjusted by changing the pressure difference between the refrigerant suction pressure in the cylinder bore 11 and the gas pressure in the crankcase 21 .

[0064] In addition, the front housing 20 may be provided with a drive shaft sealing area 25 to seal between the front housing 20 and the drive shaft 50, thereby preventing leakage of refrigerant and pressure. The sealing area 25 is provided with a sealing member 26 installed between the front housing 20 and the drive shaft 50 to seal between the front housing 20 and the drive shaft 50. A radial bearing 27 may be installed on one side of the sealing member 26.

[0065] In the following, reference will be made to Figures 5 to 7 A configuration for supplying oil contained in the refrigerant in the crankcase 21 to the sealing area 25 is described in detail.

[0066] To this end, the present invention may include: a plurality of flow grooves 220 formed on the inner wall surface of the front housing 20 to enable oil to flow through the front housing 20; a connecting groove 240 formed on the inner wall surface of the front housing 20 to connect the plurality of flow grooves 220; and at least one oil supply hole 260 configured to connect the connecting grooves 240 and the sealing area 25 in which the sealing member 26 is installed to supply oil to the sealing area 25. The inner wall surface of the front housing 20 is a wall surface provided to face the rotor 60 in the front housing 20.

[0067] The plurality of flow grooves 220 are radially formed on the inner wall surface of the front housing 20. Furthermore, the plurality of flow grooves 220 are preferably formed in the upper portion of the front housing 20, but are not limited thereto. Therefore, oil that strikes the inner wall surface of the front housing 20 when the rotor 60 rotates can smoothly flow along the plurality of flow grooves 220 to the connecting groove 240 by its own weight.

[0068] Specifically, before the compressor operates, most of the oil is in a liquid state and collects on the bottom surface of the crankcase 21 by its own weight. When the compressor operates, the rotor 60, swash plate 70, and other components rotate, coating the rotating bodies with oil. The oil is then ejected in all directions by centrifugal force, resulting in a large amount of oil being located in radial areas rather than in the central area centered around the drive shaft 50. In this case, since a plurality of flow grooves 220 are radially formed in the upper portion of the front housing 20 as described above, the liquid oil adhering to the inner wall surface of the front housing 20 flows downward from the upper portion by its own weight, being smoothly supplied through the flow grooves 220.

[0069] In this case, an oil collecting portion 210 may be further provided, which is formed radially outside each of the flow grooves 220 and connected to the flow grooves 220 and has a width that narrows toward the flow grooves 220. The oil collecting portion 210 may be formed to have a greater width than the flow grooves 220 and to narrow toward the flow grooves 220, so that the oil ejected in the radial direction of the front housing 20 due to the rotation of the rotor 60 flows downward along the inner wall surface of the front housing 20 to be collected and smoothly supplied to the flow grooves 220.

[0070] In addition, according to an embodiment, the plurality of flow grooves 220 may be formed to be inclined in the same direction as the rotation direction of the rotor 60 so that a greater amount of oil can flow through the flow grooves when the rotor 60 rotates.

[0071] In the present embodiment, three flow grooves 220 are radially formed in the upper portion of the front housing 20 .

[0072] Connecting grooves 240 are formed on the inner wall surface of the front housing 20 in a circumferential direction around the insertion hole 23 into which the drive shaft 50 is inserted. Connecting grooves 240 may be formed in the upper portion of the front housing 20 so that both ends are blocked by boundary portions 29 to prevent oil from flowing. In other words, both ends of the connecting groove 240 through which oil flows by its own weight are blocked by boundary portions 29. Boundary portions 29 may correspond to the inner wall surface of the front housing 20 that does not have a groove.

[0073] To this end, in this embodiment, the connection groove 240 can be formed in a semicircular shape in the upper portion of the front housing 20, rather than a circular shape connected in the circumferential direction. However, the present invention is not limited thereto, and the connection groove 240 can of course be formed to be shorter than a semicircle.

[0074] In this case, one or more oil supply holes 260 are formed in the connecting groove 240 and connect both ends of the connecting groove 240 and the sealing area 25. Specifically, in the present embodiment, two oil supply holes 260 are formed, and each of the two oil supply holes 260 can connect both ends of the connecting groove 240 blocked by the boundary portion 29 to the sealing area 25.

[0075] While the oil supply holes 260 can be formed through a separate drilling process, the flow grooves 220 can be formed at once by die casting. Therefore, the number of oil supply holes 260 can be less than the number of flow grooves 220, and processing time and cost can be reduced.

[0076] In addition, it is preferable that the width of the connection groove 240 is greater than or equal to the diameter of the oil supply hole 260. The reason for this is that when the width of the connection groove is smaller than the diameter of the oil supply hole, the function of supplying oil cannot be smoothly performed.

[0077] In the present invention, the flow groove 220, the connecting groove 240, and the oil supply hole 260 are blocked by the race 120a of the thrust bearing member. That is, among the races formed in an annular shape—specifically, the pair of races 120a and 120b—the race 120a positioned close to the inner wall surface of the front housing 20 can be located on the inner wall surface of the front housing 20 and can cover the flow groove 220, the connecting groove 240, and the oil supply hole 260, thereby forming a closed oil chamber between the flow groove 220, the connecting groove 240, and the oil supply hole 260.

[0078] By forming the closed oil chamber as described above, the oil flowing through the flow groove 220 and the connection groove 240 can be stored in the oil chamber without flowing to another place, and can be smoothly supplied to the oil supply hole 260. When the closed oil chamber is not formed, only a portion of the oil flowing through the groove can be supplied to the oil supply hole, and the remaining oil may flow toward the opened rotor 60, resulting in insufficient oil supply to the sealing area.

[0079] In addition, in the present invention, the oil flow is blocked by the boundary portion 29 at both ends of the connecting groove 240, and the oil supply hole 260 connects the two ends of the connecting groove 240 and the sealing area 25, so that the oil flowing through the flow groove 220 and the connecting groove 240 is supplied immediately, rather than being supplied after being filled to the position of the oil supply hole 260 in the oil chamber.

[0080] In this case, when the seat ring 120a covers the flow groove 220, the connecting groove 240 and the oil supply hole 260 to form an oil chamber, the oil supply hole 260 is preferably formed radially outward from the boss portion 20a protruding from the inner wall surface of the front housing 20 to ensure a sealed section.

[0081] In this embodiment, the seat ring 120a covers all of the flow groove 220, the connection groove 240, and the oil supply hole 260 to form an oil chamber, but the present invention is not limited thereto. That is, the seat ring may cover only the connection groove, or may cover at least a portion of the flow groove or at least a portion of the oil supply hole excluding the connection groove to form an oil chamber.

[0082] In addition, according to an embodiment of the present invention, a circulation groove 320 and an extension groove 340 formed in the inner wall surface of the front housing 20 to circulate oil may be further included.

[0083] The circulation groove 320 may be provided on an opposite side of the connecting groove 240 relative to the boundary portion 29. Like the connecting groove 240, the circulation groove 320 may be formed in the inner wall surface of the front housing 20 in a circumferential direction around the insertion hole 23 into which the drive shaft 50 is inserted.

[0084] Specifically, the circulation groove 320 may be formed in a lower portion of the front housing 20 in a substantially semicircular shape substantially symmetrical to the connection groove 240 so that leaked oil may be stored between the inner wall surface of the front housing 20 and the seat ring 120a.

[0085] The extension groove 340 may extend radially from the circulation groove 320. Therefore, the oil in the circulation groove 320 may flow toward the lower side into the radially connected extension groove 340 by its own weight and may be discharged to the crankcase 21 again.

[0086] As described above, the circulation groove 320 and the extension groove 340 are formed so that oil is supplied to the race 120 a and, at the same time, the oil is discharged back to the crankcase 21 to achieve oil circulation.

[0087] exist Figure 8 , an embodiment is shown in which the circulation groove 320 and the extension groove 340 are omitted, and only the flow groove 220 , the connection groove 240 , and the oil supply hole 260 are formed in the inner wall surface of the front housing 20 .

[0088] According to the present invention, since a large amount of oil can be smoothly supplied to the sealing area of ​​the drive shaft of the front housing, the temperature of frictional heat between the drive shaft and the sealing member can be reduced, thereby preventing leakage of refrigerant and pressure and improving durability.

[0089] The present invention is not limited to the specific embodiments and descriptions described above, and any person skilled in the art may make various modifications without departing from the subject matter of the invention as claimed in the claims, and the modifications are within the scope defined by the claims.

[0090] Industrial Applicability

[0091] The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor capable of smoothly supplying oil contained in a refrigerant in a crankcase to a sealing area of ​​a drive shaft of a front housing to reduce the temperature of frictional heat between the drive shaft and a sealing member, prevent leakage of refrigerant and pressure, and improve durability.

Claims

1. A variable displacement swash plate type compressor comprising: a front housing and a rear housing; a cylinder body coupled between the front housing and the rear housing; a drive shaft rotatably mounted in the front housing and the cylinder block; a rotor coupled to the drive shaft for rotation therewith; a swash plate slidably coupled to the rotor and mounted on the drive shaft such that an inclination angle of the swash plate is adjustable; a sealing member installed between the drive shaft and the front housing to seal between the drive shaft and the front housing; a plurality of flow grooves formed in an inner wall surface of the front housing, the plurality of flow grooves through which oil flows; a connecting groove formed in the inner wall surface of the front housing and connecting the plurality of flow grooves; at least one or more oil supply holes configured to connect the connection groove and a sealing area in which the sealing member is installed to supply the oil to the sealing area; as well as a seat ring provided on the inner wall surface of the front housing to cover the connecting groove, thereby forming an oil chamber communicating with the at least one or more oil supply holes, wherein both ends of the connecting groove are blocked by boundary portions to prevent the oil from flowing, Furthermore, the variable displacement swash plate type compressor further comprises: a circulation groove formed in the inner wall surface of the front housing to circulate the oil; wherein the circulation groove is provided on an opposite side of the connecting groove relative to the boundary portion, and wherein the circulation groove is not connected to the plurality of flow grooves and the at least one or more oil supply holes.

2. The variable displacement swash plate type compressor according to claim 1, wherein: The seat ring covers at least a portion of the plurality of flow grooves.

3. The variable displacement swash plate type compressor according to claim 1, wherein: The seat ring covers at least a portion of the at least one or more oil supply holes.

4. The variable displacement swash plate type compressor according to claim 1, wherein: The at least one or more oil supply holes are formed in the connecting groove.

5. The variable displacement swash plate type compressor according to claim 1, wherein: The plurality of flow grooves are radially formed in the inner wall surface of the front housing.

6. The variable displacement swash plate type compressor according to claim 1, wherein: The plurality of flow grooves are formed in an upper portion of the front housing.

7. The variable displacement swash plate type compressor according to claim 1, wherein: The connecting groove is formed in the inner wall surface of the front housing in a circumferential direction around an insertion hole into which the drive shaft is inserted.

8. The variable displacement swash plate type compressor according to claim 1, wherein: The connecting groove is formed in an upper portion of the front housing.

9. The variable displacement swash plate type compressor according to claim 4, wherein: The connection groove may have a width greater than or equal to a diameter of the at least one or more oil supply holes.

10. The variable displacement swash plate type compressor according to claim 1, wherein The number of the at least one or more oil supply holes is less than the number of the plurality of flow grooves.

11. The variable displacement swash plate type compressor according to claim 1, wherein: The at least one or more oil supply holes connect both ends of the connecting groove to the sealing area.

12. The variable displacement swash plate type compressor according to claim 1, wherein: The at least one or more oil supply holes are formed radially outward from a boss portion protruding from the inner wall surface of the front housing.

13. The variable displacement swash plate type compressor according to claim 1, wherein: The circulation groove is formed in the inner wall surface of the front housing in a circumferential direction around an insertion hole into which the drive shaft is inserted.

14. The variable displacement swash plate type compressor according to claim 13, further comprising: An extension groove extends radially from the circulation groove.

15. The variable displacement swash plate type compressor according to claim 1, wherein A radial bearing configured to rotatably support the drive shaft is also mounted in the sealing area.

16. The variable displacement swash plate type compressor according to claim 5, further comprising: An oil collecting portion is connected to the plurality of flow grooves radially outward from the plurality of flow grooves and has a width that narrows toward the plurality of flow grooves.

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