Reciprocating compressor

Abstract

Disclosed is a reciprocating compressor. The reciprocating compressor comprises a shell, a drive motor, a drive shaft, and a connecting rod, wherein the connecting rod is provided with a discharge guiding portion. The discharge guiding portion is provided at a first end portion of the connecting rod and periodically communicated with an oil flow path of the drive shaft, and the discharge guiding portion may be formed on the opposite side from a piston. Accordingly, foreign matter that has flowed in and reached the bearing surface between the drive shaft and the connecting rod can be easily discharged to the inner space of the shell via the discharge guiding portion without a decrease in the load-bearing capacity at the bearing surface.

Description

reciprocating compressor

[0001] The present invention relates to a reciprocating compressor.

[0002] Compressors can be categorized into several types, including rotary compressors, scroll compressors, and reciprocating compressors, depending on the compression method and type of refrigerant used. Reciprocating compressors compress the refrigerant through the reciprocating motion of a piston in a cylinder.

[0003] Reciprocating compressors can be categorized into vibrating and coupled types, depending on the piston actuation method. In an oscillating reciprocating compressor, the piston is connected to the actuator of a reciprocating motor and vibrates, reciprocating within a cylinder to compress the refrigerant. In a coupled reciprocating compressor, the piston is connected to the shaft of a rotary motor and reciprocates within a cylinder to compress the refrigerant.

[0004] In a vibrating reciprocating compressor, the suction side and the discharge side may be arranged on one side of the piston or on both sides, but in the case of a coupled reciprocating compressor, the suction side and the discharge side are mostly arranged on one side of the piston. The present invention relates to a coupled reciprocating compressor, and a reciprocating compressor may be defined as a coupled reciprocating compressor hereinafter.

[0005] Reciprocating compressors can be categorized into lower-compression and upper-compression types based on the relative positions of the motor and compressor. In the lower-compression type, the compression unit is located below the motor, while in the upper-compression type, the compression unit is located above the motor.

[0006] The lower compression method, with its compression unit located adjacent to the oil stored in the shell, is advantageous for lubrication. However, the space for the loop pipe is limited, and its submersion in the oil can reduce oil viscosity. Conversely, the upper compression method, with its greater distance between the compression unit and the oil, presents a disadvantage for lubrication. However, its wider installation space and the absence of oil submersion in the loop pipe can be advantageous for maintaining oil viscosity.

[0007] The reciprocating compressor disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2005-163775) has an oil passage formed at the lower end of a drive shaft with an oil feeder, and an oil supply hole and an oil supply groove formed in succession on the outer surface of the drive shaft that communicate with the oil passage. Accordingly, oil is guided to the upper end of the drive shaft through the oil supply hole and / or the oil supply groove, and is supplied to the compression unit while spraying from the upper end of the drive shaft, and at the same time, can be supplied between the oil supply hole and the connecting rod coupled to the eccentric pin portion of the drive shaft.

[0008] However, in Patent Document 1, the oil supply hole and / or oil supply groove connected to the outer surface of the eccentric pin portion of the drive shaft is blocked by the large part of the connecting rod, so that dirt transmitted through the oil supply hole may cause wear between the drive shaft and the connecting rod.

[0009] The reciprocating compressor disclosed in Patent Document 2 (Chinese Publication No. 201721591721) has a fly groove formed in the major portion of the connecting rod so that the oil supply hole and / or oil supply groove provided in the eccentric pin portion of the drive shaft can be connected to the internal space of the shell. Accordingly, waste delivered through the oil supply hole and / or oil supply groove can be discharged into the internal space of the shell.

[0010] However, Patent Document 2 discloses that oil supplied between the drive shaft and the connecting rod may easily leak between the drive shaft and the connecting rod, hindering smooth oil supply to the entire bearing surface between the drive shaft and the connecting rod. This may increase frictional loss between the drive shaft and the connecting rod.

[0011] In addition, Patent Document 2 has a spray groove formed facing the piston so that the oil supplied between the drive shaft and the connecting rod is smoothly sprayed to the compression section. However, this may result in insufficient oil in the pressurized section between the drive shaft and the connecting rod during the discharge stroke when the gas force increases, making it impossible to sufficiently form the fluid pressure. This may result in a decrease in the load-bearing capacity of the bearing between the drive shaft and the connecting rod, which may deteriorate the reliability of the bearing.

[0012] The purpose of the present invention is to provide a reciprocating compressor that can prevent oil supplied between a drive shaft and a connecting rod from easily leaking between the drive shaft and the connecting rod, while allowing contaminants mixed in the oil to be quickly discharged between the drive shaft and the connecting rod.

[0013] Another object of the present invention is to provide a reciprocating compressor capable of preventing waste discharged between a drive shaft and a connecting rod from flying toward a compression section.

[0014] Another object of the present invention is to provide a reciprocating compressor in which a discharge guide portion is formed between a driving shaft and a connecting rod, and the discharge guide portion is formed in an area that does not lower the bearing load support capacity between the driving shaft and the connecting rod.

[0015] Another object of the present invention is to provide a reciprocating compressor in which a discharge guide portion is formed between a driving shaft and a connecting rod, and the discharge guide portion is formed in an area where waste can be discharged before a dynamic pressure lower than the pressure of an oil passage is generated.

[0016] In order to achieve the object of the present invention, a reciprocating compressor including a shell, a drive motor, a drive shaft, and a connecting rod, wherein the connecting rod is provided with a discharge guide portion. Oil may be stored in an internal space of the shell. The drive motor may be provided in the internal space of the shell. The drive shaft may be coupled to a rotor of the drive motor. An oil passage may be provided to suck up and scatter oil stored in the shell. A first end of the connecting rod is coupled to the drive shaft, and a second end of the connecting rod, which forms an end opposite to the first end, is coupled to a piston to transmit the rotational force of the drive shaft to the piston. The discharge guide portion may be provided at the first end of the connecting rod and may be periodically connected with the oil passage of the drive shaft. Through this, foreign substances transmitted through the oil passage may be discharged into the internal space of the shell through the discharge guide portion, thereby suppressing wear on a bearing surface between the drive shaft and the connecting rod.

[0017] In this case, when the first center line passing through the reciprocating center of the piston is referred to as the first center line, and the center line perpendicular to the first center line from the center of the first end of the connecting rod is referred to as the second center line, the discharge guide portion may be formed on the opposite side of the piston with respect to the second center line. Through this, the load-bearing capacity between the driving shaft and the connecting rod can be increased, while foreign substances discharged through the discharge guide portion can be suppressed from flying toward the piston and cylinder.

[0018] For example, the discharge guide portion may be formed within a range of 120° to 270° based on the bearing angle of the first end of the connecting rod at a first position where the connecting rod is parallel to the first center line. Through this, foreign substances that have entered the bearing surface between the driving shaft and the connecting rod can be easily discharged into the internal space of the shell through the discharge guide portion without reducing the load-bearing capacity of the bearing surface.

[0019] As another example, the discharge guide portion may be formed within a range of (120° - maximum rotation angle of the first end) to (270° - maximum rotation angle of the first end) based on the bearing angle of the first end of the connecting rod at a second position where the first end of the connecting rod is rotated to the maximum about the first center line centered on the second end of the connecting rod. Through this, foreign substances that have entered the bearing surface between the driving shaft and the connecting rod can be easily discharged into the internal space of the shell through the discharge guide portion without reducing the load-bearing capacity of the bearing surface.

[0020] As another example, the discharge guide portion may be recessed into the inner surface of the first end portion by a predetermined depth and may be opened at least at one of the axial ends of the first end portion to form a discharge end. Accordingly, while the second refueling groove is in communication with the discharge guide portion, foreign substances transmitted through the second refueling groove can be smoothly discharged into the internal space of the shell through the discharge guide portion.

[0021] For example, the discharge guide portion may be formed so that the cross-sectional area of ​​the discharge end is the same as the cross-sectional area of ​​the side communicating with the oil passage. Through this, the discharge guide portion can be easily processed.

[0022] In addition, the discharge guide may be formed so that the cross-sectional area of ​​the discharge end is larger than the cross-sectional area of ​​the side communicating with the oil passage. Accordingly, the cross-sectional area of ​​the discharge guide increases as it approaches the discharge end, allowing foreign substances to be discharged more quickly into the internal space of the shell.

[0023] In addition, the discharge guide portion may extend in the axial direction of the driving shaft. Accordingly, since discharge ports are provided at each end of the discharge guide portion, foreign substances can be quickly discharged through both discharge ports.

[0024] In addition, the discharge guide portion may be formed to be inclined in the direction of rotation of the drive shaft. This allows foreign substances to be quickly discharged by centrifugal force even without forming the discharge guide portion wide, thereby reducing the surface pressure on the bearing surface and improving the bearing's support capacity.

[0025] In addition, the exhaust guide portion may be formed to be inclined in a direction opposite to the rotational direction of the driving shaft. This can minimize foreign substances discharged through the exhaust guide portion from flying between the cylinder and piston and / or toward the suction muffler.

[0026] As another example, the discharge guide portion may be formed to penetrate from the inner surface to the outer surface of the first end portion. This allows foreign substances discharged through the discharge guide portion to be discharged radially from the middle of the connecting rod, thereby reducing the scattering distance.

[0027] For example, the discharge guide portion may be formed to penetrate the upper half of the first end portion. This allows the length of the second oil supply groove to be sufficiently secured, thereby maintaining the amount of oil supplied to the second bearing surface.

[0028] As another example, the drive shaft may be provided with an eccentric pin portion into which the first end of the connecting rod is rotatably inserted, and an oil supply groove forming a part of the oil passage may be formed on the outer surface of the eccentric pin portion. The oil supply groove may be formed to be lower than or equal to the axial upper end of the first end. Through this, the oil flowing between the drive shaft and the connecting rod may be minimized from leaking from the bearing surface between the drive shaft and the connecting rod, thereby improving lubrication performance.

[0029] For example, the circumferential width of the discharge guide portion may be formed to be greater than or equal to the circumferential width of the oil supply groove. This can prevent oil supplied to the oil supply groove from excessively flowing out from the bearing surface between the drive shaft and the connecting rod through the discharge guide portion.

[0030] A reciprocating compressor according to the present embodiment comprises a shell, a drive motor, a drive shaft, and a connecting rod, wherein the connecting rod is provided with a discharge guide, and the discharge guide is provided at a first end of the connecting rod so as to be periodically communicated with an oil passage of the drive shaft. The discharge guide may be formed on the opposite side of the piston. Through this, foreign substances transmitted through the oil passage are discharged into the internal space of the shell through the discharge guide, thereby suppressing wear on the bearing surface between the drive shaft and the connecting rod.

[0031] In the reciprocating compressor according to the present embodiment, the discharge guide portion can be formed within a range of 120° to 270° based on the direction of the load received by the first end of the connecting rod at a first position parallel to the first center line of the connecting rod. Through this, the load-bearing capacity of the bearing surface between the drive shaft and the connecting rod is not reduced, and foreign substances that have entered the bearing surface can be easily discharged into the internal space of the shell through the discharge guide portion.

[0032] In the reciprocating compressor according to the present embodiment, the discharge guide portion may be recessed to a predetermined depth in the inner circumference of the first end portion, and may be opened at least at one of the axial ends of the first end portion to form a discharge end. Accordingly, while the oil supply groove provided on the drive shaft is in communication with the discharge guide portion, foreign substances transmitted through the oil supply groove may be smoothly discharged into the internal space of the shell through the discharge guide portion.

[0033] In the reciprocating compressor according to the present embodiment, an oil supply groove is formed on the outer surface of the eccentric pin portion of the drive shaft, and the oil supply groove may be formed at or below the axial upper end of the first end portion. This minimizes oil flowing between the drive shaft and the connecting rod from leaking out from the bearing surface between the drive shaft and the connecting rod, thereby improving lubrication performance.

[0034] Fig. 1 is a cross-sectional view showing the inside of a reciprocating compressor according to the present embodiment.

[0035] Fig. 2 is a perspective view showing the drive shaft and connecting rod in an exploded view in a reciprocating compressor according to the present embodiment.

[0036] Figure 3 is a perspective view showing the drive shaft and connecting rod assembled in Figure 2.

[0037] Fig. 4 is a front view showing a portion of the connecting rod in Fig. 3 broken off.

[0038] Fig. 5 is a plan view illustrating the location of the discharge guide according to the present embodiment.

[0039] Figure 6 is a graph comparing the position of the discharge guide according to the present embodiment with the bearing dynamic pressure.

[0040] Fig. 7 is a graph comparing the bearing loads by position for the discharge guide according to the present embodiment.

[0041] Figure 8a is a graph showing changes in bearing input according to operating speed for the discharge guide unit according to the present embodiment.

[0042] Figure 8b is a graph showing changes in compressor efficiency according to operating speed for the exhaust guide unit according to the present embodiment.

[0043] Fig. 9 is a front view showing a portion of the connecting rod broken off to illustrate another embodiment of the exhaust guide section.

[0044] FIGS. 10a and 10b are front views showing a portion of the connecting rod broken off to illustrate further embodiments of the exhaust guide portion.

[0045] Fig. 11 is a front view showing a portion of the connecting rod broken off to illustrate another embodiment of the exhaust guide section.

[0046] Fig. 12 is a front view showing a portion of the connecting rod broken off to illustrate another embodiment of the exhaust guide section.

[0047] Hereinafter, a reciprocating compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings. In the following description, the compression chamber side, centered around the piston, is defined as the front, and the opposite side as the rear. In conjunction with this, the muffler assembly is described by defining the side facing the shell as the front, and the side facing away from the shell as the rear.

[0048] Fig. 1 is a cross-sectional view showing the inside of a reciprocating compressor according to the present embodiment.

[0049] Referring to FIG. 1, a reciprocating compressor according to the present embodiment may include a shell (110) forming an exterior, an electric motor (120) provided in an internal space (110a) of the shell (110) and providing driving force, a compression unit (130) receiving driving force from the electric motor (120) to compress refrigerant, an intake / discharge unit (140) guiding refrigerant to a compression chamber (130a) and discharging the compressed refrigerant, and a damping unit (150) that buffers impact generated when a collision occurs between the shell (110) and the compressor body (C).

[0050] The shell (110) may include a lower shell (111) and an upper shell (112). The lower shell (111) and the upper shell (112) may be combined to form a sealed internal space (110a). The internal space (110a) of the shell (110) may accommodate a power unit (120) and a compression unit (130). The shell (110) may be made of a lightweight aluminum alloy (hereinafter, abbreviated as aluminum) having a high thermal conductivity.

[0051] The lower shell (111) can be formed in a roughly hemispherical shape. The bottom surface of the lower shell (111) is formed relatively flat so that the lower end of the support spring (123) described later is fixed, and an appropriate amount of oil can be stored inside the lower shell (111).

[0052] The upper shell (112) can be formed in a roughly hemispherical shape like the lower shell (111). The upper shell (112) can be joined to the lower shell (111) on the upper side of the lower shell (111) to form the internal space (110a) of the shell (110) described above.

[0053] Referring to Fig. 1, the electric motor (or driving motor) (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) may be elastically supported against the inner space (110a) of the shell (110), i.e., the bottom surface of the lower shell (111), and the rotor (122) may be rotatably installed inside the stator (121).

[0054] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0055] The stator core (1211) is made of a metal material such as electrical steel, and when voltage is applied from the outside to the electric part (120), it performs electromagnetic interaction through electromagnetic force together with the stator coil (1212) and rotor (122) described later.

[0056] The stator core (1211) is formed in a roughly rectangular shape. For example, the inner circumference of the stator core (1211) may be formed in a circular shape, and the outer circumference may be formed in a rectangular shape. The stator core (1211) may be fixed to the lower surface of a cylinder block (131), which will be described later, by a stator fastening bolt (not shown).

[0057] The stator core (1211) can be flexibly supported by a support spring (123) at the lower end of the stator core (1211) relative to the bottom surface of the shell (110) while being spaced apart axially and radially from the inner surface of the shell (110). Accordingly, vibrations generated during operation can be suppressed from being directly transmitted to the shell (110).

[0058] The stator coil (1212) may be wound inside the stator core (1211). As described above, when voltage is applied from the outside, the stator coil (1212) generates an electromagnetic force and performs an electromagnetic interaction with the stator core (1211) and the rotor (122). Through this, the electric motor (120) generates a driving force for the reciprocating motion of the compression unit (130).

[0059] The rotor (122) may include a rotor core (1221) and a magnet (1222).

[0060] The rotor core (1221), like the stator core (1211), is made of a metal material such as electrical steel and can be formed into a roughly cylindrical shape. A drive shaft (125), which will be described later, can be press-fitted and joined to the center of the rotor core (1221).

[0061] The magnet (1222) is made of a permanent magnet and can be inserted and coupled at equal intervals along the circumference of the rotor core (1221). Accordingly, when voltage is applied, the rotor (122) rotates through electromagnetic interaction with the stator core (1211) and the stator coil (1212).

[0062] The driving shaft (125) may include a shaft portion (125a), an eccentric mass portion (125b), and an eccentric pin portion (125c). The shaft portion (125a) is a portion that is inserted into an axle hole (1313a) of a cylinder block (131) to be described later and supported radially, the eccentric mass portion (125b) is a portion that extends eccentrically in the radial direction from the shaft portion (125a), and the eccentric pin portion (125c) is a portion to which a large end (hereinafter, a first end) (1261) of a connecting rod (126) to be described later is rotatably coupled. Accordingly, when the drive shaft (125) rotates together with the rotor (122), the rotational force is transmitted to the connecting rod (126) through the shaft portion (125a) and the eccentric pin portion (125c), so that the connecting rod (126) reciprocates together with the piston (132).

[0063] An oil passage (1251) may be formed on the inner and / or outer surface of the drive shaft (125), and an oil feeder (and / or oil pump) (1255) may be provided at the lower end of the oil passage (1251). Accordingly, oil pumped from the oil feeder (and / or oil pump) (1255) is sucked along the oil passage (1251) to lubricate each bearing surface (not shown) and at the same time, while spraying from the upper end of the drive shaft (125), lubricates the compression unit (125a) or cools the transmission unit (120).

[0064] A part of the oil passage (1251) may be formed in a hole shape that is sunken into the inside of the drive shaft (125) in an axial or diagonal direction, and another part of the oil passage (1251) may be formed in a groove shape that is sunken into the outer surface of the drive shaft (125) and extends in a spiral shape. These hole-shaped oil passages (1251) and groove-shaped oil passages (1251) may be continuously connected to each other and may extend to the upper end of the drive shaft (125), that is, to the eccentric pin portion (125c). Accordingly, each bearing surface (B1) (B2) between the shaft portion (125a) of the drive shaft (125) and the cylinder block (131) and / or between the eccentric pin portion (125c) of the drive shaft (125) and the connecting rod (126) can be smoothly lubricated.

[0065] For example, a first oil supply groove (1252a) may be formed spirally along the outer surface of the upper half of the shaft portion (125a) of the drive shaft (125), and a second oil supply groove (1252b) may be formed inclined or axially along the outer surface of the lower half of the eccentric pin portion (125c) of the drive shaft (125). In other words, the first oil supply groove (1252a) may be formed between the shaft portion (125a) of the drive shaft (125) and the shaft receiving portion (1313) of the cylinder block (131) that faces it, which will be described later, and the second oil supply groove (1252b) may be formed between the eccentric pin portion (125c) of the drive shaft (125) and the first end (1261) of the connecting rod (126) that faces it, which will be described later. Accordingly, the first oil supply groove (1252a) lubricates the first bearing surface (B1) between the shaft portion (125a) of the drive shaft (125) and the shaft portion (1311) of the cylinder block (131) to be described later, while the second oil supply groove (1252b) lubricates the second bearing surface (B2) between the eccentric pin portion (125c) of the drive shaft (125) and the first end portion (1261) of the connecting rod (126) to be described later. The oil passage (1251) will be described again later together with the discharge guide portion (1265).

[0066] The connecting rod (126) may include a first end (1261), a second end (1262), and a connecting rod portion (1263) connecting the first end (1261) and the second end (1262) to each other. The first end (1261) is a portion that is rotatably coupled to an eccentric pin portion (125c) of a drive shaft (125), and the second end (1262) is a portion that is rotatably coupled to a piston (132). In other words, the first end (1261) is a portion that rotates together with the drive shaft (125), and the second end (1262) is a portion that moves linearly together with the piston (132). Accordingly, the first end (1261) may be understood to perform a kind of cold movement with respect to the second end (1262).

[0067] The first end (1261) extends in a circular shape from one end of the connecting rod portion (1263), and the inner circumference (1261a) of the first end (1261) may be formed in a circular cross-section. In this case, the inner diameter of the first end (1261) may be formed to be slightly larger than the outer diameter of the eccentric pin portion (125c). Accordingly, the inner circumference (1261a) of the first end (1261) may perform a rotational motion (or a rotational motion relative to the second end) while making sliding contact with the outer circumference of the eccentric pin portion (125c).

[0068] In addition, a discharge guide portion (or foreign matter discharge portion) (1265) is formed on the inner surface (1261a) of the first end portion (1261), and the discharge guide portion (1265) may be opened to the upper end of the first end portion (1261) and / or the lower end of the first end portion (1261) to form a discharge portion (1265a). Accordingly, foreign matter (dirt) flowing into the second bearing surface (B2) together with oil through the second oil supply groove (1252b) can be quickly discharged from the second bearing surface (B2), thereby suppressing wear on the second bearing surface (B2).

[0069] For example, the discharge guide portion (1265) may be formed to be recessed to a preset depth in the inner surface (1261a) of the first end portion (1261), but may be formed to periodically communicate with at least a portion of the second oil supply groove (1252b). In other words, the discharge guide portion (1265) may be formed to have a circumferential width (L2) shorter than the circumferential width (L1) of the first end portion (1261) of the connecting rod (126) forming the major portion, but may be formed to communicate with the second oil supply groove (1252b) at a specific section when the driving shaft (125) rotates. Accordingly, it is possible to suppress oil supplied to the second oil supply groove (1252b) from excessively leaking out from the second bearing surface (B2) through the discharge guide portion (1265). The shape and / or formation range of the discharge guide (1265) will be described again later together with the second fuel refueling groove (1252b).

[0070] The second end (1262) extends annularly from the other end of the connecting rod (1263), and the inner diameter of the second end (1262) may be formed smaller than the inner diameter of the first end (1261). Accordingly, the first end (1261) may be defined as a large end, and the second end (1262) may be defined as a small end. Hereinafter, the large end of the connecting rod (126) will be defined as the first end (1261), and the small end as the second end (1262), respectively, and described.

[0071] The connecting rod portion (1263) is a portion connecting the first end (1261) and the second end (1262), and may be formed to become increasingly narrower from the first end (1261) toward the second end (1262). The connecting rod portion (1263) may be formed as a solid bar or frame, and in some cases, may be formed as a hollow shape having a lubrication hole (not shown) to connect the inner surface (1261a) of the first end (1261) and the inner surface (not shown) of the second end (1262). This embodiment shows an example in which the connecting rod portion (1263) is formed as a solid bar or frame. Accordingly, it is possible to suppress dirt or foreign substances transmitted to the second bearing surface from flowing toward the cylinder (1315) and the piston (132).

[0072] Referring to FIG. 1, the compression unit (130) according to the present embodiment may include a cylinder block (131) and a piston (132). The cylinder block (131) is elastically supported on a shell (110), and the piston (132) is coupled to a drive shaft (125) by a connecting rod (126) and moves relative to the cylinder block (131).

[0073] The cylinder block (131) may be provided on one axial side of the electric motor (120), for example, on the upper side. The cylinder block (131) is fastened to the stator (121) with a stator fastening bolt (not shown), and may be elastically supported on the lower shell (111) together with the stator (121) of the electric motor (120).

[0074] The cylinder block (131) according to the present embodiment may include a frame portion (1311), a fixed projection portion (1312) coupled to a stator (121) of a power unit (120), a shaft portion (1313) supporting a drive shaft (125), a bearing receiving groove portion (1314) provided around the shaft portion (1313) to receive a thrust bearing (160) to be described later, and a cylinder portion (cylinder) (1315) forming a compression chamber (130a).

[0075] The frame portion (1311) may be formed in a flat shape extending in the transverse direction, or may be formed in a radial shape by having a portion of the edge except for the corners processed to be thin.

[0076] The fixed protrusion (1312) may be formed at the edge of the frame portion (1311). For example, the fixed protrusion (1312) may be formed to protrude downward from the edge of the frame portion (1311) toward the power unit (120).

[0077] The shaft member (1313) can be formed to extend axially on both sides from the central portion of the frame member (1311). An shaft hole (1313a) is formed to penetrate the shaft member (1313) in the axial direction so that the drive shaft (125) can pass through it, and a bushing bearing (not shown) can be inserted and coupled to the inner circumferential surface of the shaft hole (1313a).

[0078] A cylinder portion (hereinafter, abbreviated as cylinder) (1315) may be formed radially eccentrically from one edge of a frame portion (1311). A piston (132) connected to a connecting rod (126) may be inserted into the inner opening of the cylinder (1315) through the radial direction, and a valve assembly (141) forming an intake / exhaust portion (140) to be described later may be mounted on the outer opening.

[0079] The piston (132) may be formed flat with an open side (rear side) facing the connecting rod (126), while the opposite side (front side) facing away from the connecting rod (126) is closed. Accordingly, the connecting rod (126) is inserted into the rear side of the piston (132) and rotatably coupled, and the front side of the piston (132) forms a compression chamber (130a) inside the cylinder (1315) together with the valve assembly (141) described later.

[0080] Referring to FIG. 1, the suction / discharge unit (140) according to the present embodiment may include a valve assembly (141), a muffler assembly (142), and a clamping member (143).

[0081] The valve assembly (141) may include an intake valve portion (not shown) and a discharge valve portion (not shown). The intake valve portion may connect the compression chamber (130a) to an intake connection groove (not shown) of a connecting muffler (not shown) to be described later, and the discharge valve portion may connect the compression chamber (130a) to an exhaust connection groove (not shown) of a connecting muffler (not shown) to be described later. Accordingly, the intake valve portion and the discharge valve portion may be formed to be adjacent to each other on a plane.

[0082] The muffler assembly (142) may include an intake muffler (142a) and a discharge muffler (142b). In other words, the muffler assembly (142) may be formed by combining an upper muffler and a lower muffler to form an intake space (S1) of the intake muffler (142a) and an discharge space (S2) of the discharge muffler (142b), respectively.

[0083] The clamping member (143) is provided at the front of the suction / discharge portion (140), that is, at the front surface of the muffler assembly (142), so as to fix the muffler assembly (142) to the cylinder block (131) of the compression portion (130).

[0084] The damping unit (150) is provided on the upper side of the compression unit (130) and the suction / discharge unit (140). The damping unit (150) may include a front damper (151) and a rear damper (152) which are respectively provided on both sides of the reciprocating direction of the piston (132), and the front damper (151) and the rear damper (152) may be made of an elastic material such as rubber. The front damper (151) can effectively suppress or buffer the impact caused by the collision between the compression unit (130) and the suction / discharge unit (140) and the shell (110) when the compressor is driven. The rear damper (152) can effectively suppress or buffer the impact caused by the collision between the shell (110) and the compression unit (130) when the compressor is driven.

[0085] The unexplained symbol 127 in the drawing is a balance weight.

[0086] The reciprocating compressor according to the above embodiment operates as follows.

[0087] That is, when power is applied to the electric motor (120), the rotor (122) rotates. When the rotor (122) rotates, the drive shaft (125) coupled to the rotor (122) rotates and transmits the rotational force to the piston (132) through the connecting rod (126). The piston (132) reciprocates in the forward and backward direction with respect to the cylinder (1315) by the connecting rod (126).

[0088] For example, when the piston (132) moves backward (suction stroke) in the cylinder (1315), the volume of the compression chamber (130a) increases. When the volume of the compression chamber (130a) increases, the refrigerant filled in the suction space (S1) of the muffler assembly (142) through the suction pipe (115) passes through the suction valve section of the valve assembly (141) and is sucked into the compression chamber (130a).

[0089] Conversely, when the piston (132) moves forward (discharge stroke) in the cylinder (1315), the volume of the compression chamber (130a) is reduced. When the volume of the compression chamber (130a) is reduced, the refrigerant filled in the compression chamber (130a) is compressed and discharged through the discharge valve part of the valve assembly (141) into the discharge connection groove of the connecting muffler, and the refrigerant is discharged into the discharge space (S2) forming the discharge muffler (142b) and then discharged to the refrigeration cycle through the discharge pipe (not shown), repeating a series of processes.

[0090] At the same time, the oil stored in the internal space (110a) of the shell (110) is sucked up along the oil passage (1251) of the drive shaft (125), and some of this oil is supplied to each bearing surface (B1) (B2), while some of it is sprayed from the top of the drive shaft (125) to cool the power unit (120).

[0091] At this time, the second oil supply groove (1252b) provided in the eccentric pin portion (125c) of the drive shaft (125) is formed shorter than the first oil supply groove (1252a) provided in the shaft portion (125a) in consideration of the length of the eccentric pin portion (125c), so that the upper end of the second oil supply groove (1252b) forming the outlet end may be formed higher than the axial height of the first end portion (1261) of the connecting rod (126). In other words, the upper end of the second oil supply groove (1252b) may be formed long so as to be open to the internal space (110a) of the shell (110). However, in this case, oil sucked through the second oil supply groove (1252b) may scatter toward the internal space (110a) of the shell (110) before being widely spread to the second bearing surface (B2), resulting in oil shortage at the second bearing surface (B2).

[0092] Taking this into consideration, the upper end of the second oil refill groove (1252b) may be formed only to a height that covers the first end (1261) of the connecting rod (126), so that the oil sucked in through the second oil refill groove (1252b) can be widely spread to the second bearing surface (B2). However, in this case, foreign substances mixed in the oil sucked in through the second oil refill groove (1252b) may remain on the second bearing surface (B2), causing wear.

[0093] Accordingly, in this embodiment, the upper end of the second refueling groove (1252b) is formed only to a height that is covered by the first end (1261) of the connecting rod (126), and a discharge guide (1265) is formed in the first end (1261) of the connecting rod (126) so that foreign substances transmitted through the second refueling groove (1252b) can be periodically discharged.

[0094] Fig. 2 is a perspective view showing the drive shaft and the connecting rod in the reciprocating compressor according to the present embodiment in an exploded state, Fig. 3 is a perspective view showing the drive shaft and the connecting rod in Fig. 2 in an assembled state, Fig. 4 is a front view showing a part of the connecting rod in Fig. 3 in a broken state, and Fig. 5 is a plan view showing the position of the discharge guide according to the present embodiment.

[0095] Referring to FIGS. 2 to 5, a second oil supply groove (1252b) forming part of an oil passage (1251) is formed in an eccentric pin portion (125c) of a drive shaft (125) according to the present embodiment, and a discharge guide portion (1265) may be formed on an inner surface (1261a) of a first end (1261) of a connecting rod (126) facing the second oil supply groove (1252b) to periodically communicate with the second oil supply groove.

[0096] The second oil supply groove (1252b) may be formed to be inclined with respect to the axial direction so that its lower end is connected to the second oil supply hole (1251b) that penetrates the outer surface of the eccentric pin portion (125c) from the lower half of the eccentric pin portion (125c), for example, the upper side of the eccentric mass portion (125b). In other words, the second oil supply groove (1252b) may be formed to be inclined so that its upper end is in the forward direction (i.e., in the direction of centrifugal force) with respect to the rotational direction of the drive shaft (125), for example, at an angle of approximately 15° to the rotational direction of the drive shaft (125). Accordingly, oil flowing into the second oil supply groove (1252b) can be quickly sucked from the lower end to the upper end of the second oil supply groove (1252b) by the centrifugal force.

[0097] In this case, the upper end of the second refueling groove (1252b) may be formed at a height that is covered by the first end (1261) of the connecting rod (126), that is, lower than or equal to the upper end (discharge end) (1265a) of the first end (1261) of the connecting rod (126). This embodiment illustrates an example in which the upper end of the second refueling groove (1252b) is formed lower than the upper end (discharge end) (1265a) of the first end (1261) of the connecting rod (126). Accordingly, even if a machining error and / or assembly error occurs between the drive shaft (125) and the connecting rod (126), or the behavior of the connecting rod (126) becomes unstable due to abnormal operation during compressor operation, the upper end of the second oil supply groove (1252b) can be maintained in a state where it is almost entirely covered by the first end (1261) of the connecting rod (126). This can suppress the oil sucked in through the second oil supply groove (1252b) from being excessively discharged from the second bearing surface (B2) to the internal space (110a) of the shell (110), thereby improving the lubrication performance of the second bearing surface (B2).

[0098] The discharge guide (1265) is formed on the inner surface (1261a) of the first end (1261) of the connecting rod (126), and may be formed in a groove shape that is sunken toward the outer surface by a preset depth. For example, the discharge guide (1265) may be formed in a hexahedral shape in which the lower end is closed, while the upper end (discharge end) is opened toward the inner space (110a) of the shell (110). Accordingly, oil and / or foreign substances transferred from the second oil supply groove (1252b) to the discharge guide (1265) can be recovered into the inner space (110a) of the shell (110) while being scattered from the upper end (discharge end) of the opened discharge guide (1265).

[0099] The exhaust guide portion (1265) may be formed to have the same cross-sectional area along the axial direction along the same axis as the axial direction of the driving shaft (125). In other words, the exhaust guide portion (1265) may be formed to have the same depth and cross-sectional area along the axial direction. Accordingly, the exhaust guide portion (1265) may be easily processed.

[0100] The discharge guide portion (1265) is formed along the axial direction, but may be extended to a length that allows at least a portion of it to overlap radially with the first refueling groove (1252a). Accordingly, the discharge guide portion (1265) may be periodically connected to the first refueling groove (1252a) when the driving shaft (125) rotates.

[0101] Referring to FIG. 4, the circumferential width (L2) of the discharge guide portion (1265) may be formed to be greater than or equal to the circumferential width (L1) of the first refueling groove (1252a), but may be formed to be smaller than the circumferential length of the inner surface of the first end (1261) of the connecting rod (126). Accordingly, the discharge guide portion (1265) may be periodically connected to the first refueling groove (1252a) when the driving shaft (125) rotates.

[0102] Referring to FIG. 5, the exhaust guide portion (1265) may be formed on the opposite side of the piston (132). In other words, when the first center line (CL1) passing through the reciprocating center of the piston (132) and the center line perpendicular to the first center line (CL1) from the center (Om) of the first end (1261) of the connecting rod (126) are referred to as the second center line (CL2), the exhaust guide portion (1265) may be formed on the opposite side of the piston (132) based on the second center line (CL2).

[0103] Specifically, the discharge guide portion (1265) can be formed within a range of approximately 120° to 270° based on the load direction (i.e., bearing angle) received by the first end (1261) of the connecting rod (126) at a first position where the connecting rod (126) is parallel to the first center line (CL1). In other words, the discharge guide portion (1265) can be formed within a range of (120° - maximum rotation angle of the first end) to (270° - maximum rotation angle of the first end) based on the load direction received by the first end (1261) of the connecting rod (126) at a second position where the first end (1261) of the connecting rod (126) is rotated to the maximum about the first center line (CL1) with the second end (1262) of the connecting rod (126) as the center (Os). Accordingly, foreign substances that have entered the second bearing surface (B2) can be easily discharged into the internal space (110a) of the shell (110) through the discharge guide (1265) without reducing the load-bearing capacity of the second bearing surface (B2).

[0104] Fig. 6 is a graph comparing the position of the discharge guide part according to the present embodiment with the bearing dynamic pressure, and Fig. 7 is a graph comparing the bearing load by position for the discharge guide part according to the present embodiment.

[0105] Typically, the rotation angle of the drive shaft (125) can be formed with a phase difference of 180° from the bearing angle. In other words, referring to FIGS. 6 and 7, the bearing angle when the piston (132) is located at the top dead center (TDC) can be 0°, the bearing angle when the piston (132) is located at the exact center moving from the top dead center (TDC) to the bottom dead center (BDC) can be 90°, the bearing angle when the piston (132) is located at the bottom dead center (BDC) can be 180°, and the bearing angle when the piston (132) is located at the exact center moving from the bottom dead center (BDC) to the top dead center (TDC) can be 270°.

[0106] This can be divided into four sections based on the reciprocating motion of the piston (132). That is, the bearing angle is divided into the first section (A1) between 0° and 270°, the second section (A2) between 270° and 180°, the third section (A3) between 180° and 90°, and the fourth section (A4) between 90° and 0°. The first and second sections (A1) (A2) can be defined as the suction stroke, and the third and fourth sections (A3) (A4) can be defined as the compression and discharge stroke. Accordingly, the bearing dynamic pressure for each bearing angle at the first end (1261) of the connecting rod (126) can be formed to be high in the first section (A1) in which the piston (132) moves from the top dead center (TDC) toward the bottom dead center (BDC), and to be formed to be highest in the fourth section (A4) in which the piston (132) moves from the bottom dead center (BDC) toward the top dead center (TDC).

[0107] Referring to Fig. 6, it can be seen that the bearing dynamic pressure is significantly generated during the initial suction stroke and discharge stroke of the piston (132), but that the dynamic pressure is not significantly generated between the later suction stroke and the compression stroke. In other words, it can be seen that the bearing dynamic pressure is hardly generated when the bearing angle (circumferential angle of the first end) is in the range of 120° to 270°.

[0108] Accordingly, in the present embodiment, as described above, a discharge guide portion (1265) communicating with a second lubrication groove (1252b) is formed at the first end (1261) of the connecting rod (126), and the discharge guide portion (1265) can be formed in a section where bearing dynamic pressure is hardly generated, that is, within a bearing angle range of 120° to 270°. Accordingly, foreign substances that have entered the second bearing surface (B2) through the second lubrication groove (1252b) are discharged into the internal space (110a) of the shell (110) through the discharge guide portion (1265), while minimizing the loss of dynamic pressure at the second bearing surface (B2) due to the discharge guide portion (1265), thereby preventing a decrease in the load-bearing capacity of the bearing.

[0109] This can also be seen through Fig. 7. Referring to Fig. 7, it can be seen that the load applied to the bearing is not very high in most sections (sections 1 and 2) of the suction stroke except for the initial suction stroke (bearing angle of approximately 330°) at the top dead center (TDC) of the piston (132).

[0110] And, it can be seen that the load applied to the bearing is not as high as in the first and second sections (A1) and (A2) in the initial discharge stroke (bearing angle is approximately 50°) including the bottom dead center (BDC) of the piston (132).

[0111] However, in the later discharge stroke of the piston (132) (bearing angle is approximately 50° to 60°), it can be seen that the load applied to the bearing is significantly higher than in the first to third sections (A1 to A3).

[0112] Through this, it can be seen that when the discharge guide part (1265) is formed at a stroke position (bearing angle) other than the stroke position (bearing angle) of the piston (132) where the load applied to the bearing becomes higher than a certain value, the decrease in the bearing support capacity due to the discharge guide part (1265) can be suppressed. In other words, it can be seen that it is advantageous in terms of securing the bearing support capacity to form the discharge guide part (1265) in a range of 50° to 330° based on the load direction received by the first end (1261) of the connecting rod (126), i.e., the bearing angle.

[0113] However, since the first end (1261) of the connecting rod (126) rotates with the second end (1262) as the center, it may be advantageous to form the exhaust guide (1265) considering the rotation angle of the first end (1261). For example, assuming that the first end (1261) of the connecting rod (126) rotates with respect to the first center line (CL1) by approximately ±20° to ±30° with respect to the second end (1262), it may be desirable to form the exhaust guide (1265) at a position greater than or equal to approximately 70° to 80° and less than or equal to approximately 290° to 300° based on the bearing angle.

[0114] When the discharge guide part is formed in the above location, the corresponding operational effects are as follows. Fig. 8a is a graph showing changes in bearing input according to operating speed for the discharge guide part according to the present embodiment, and Fig. 8b is a graph showing changes in compressor efficiency according to operating speed for the discharge guide part according to the present embodiment.

[0115] Referring to Fig. 8a, it can be seen that the bearing input in the present embodiment (wherein the discharge guide is formed on the opposite side of the piston with respect to the second center line) is further reduced compared to the conventional embodiment (wherein the oil supply groove and / or oil supply hole is formed on the piston side with respect to the second center line (CL2)). In particular, it can be seen that the gap with the conventional embodiment increases as the operating speed of the compressor increases. Accordingly, it can be seen that the compressor efficiency in the present embodiment is improved compared to the conventional embodiment, as shown in Fig. 8b. As with the bearing input described above, it can be seen that the compressor efficiency in the present embodiment is further improved as the operating speed increases.

[0116] The above results indicate that, in conventional low-speed operation, the bearing load on the second bearing surface (B2) does not increase significantly, so the bearing input may not increase relatively significantly. However, in high-speed operation, oil leakage from the second bearing surface (B2) increases, and the bearing support force decreases significantly, so the bearing load increases significantly, which can be interpreted as increasing the bearing input and significantly reducing the compressor efficiency.

[0117] On the other hand, in the case of this embodiment, the bearing load does not increase significantly in both low-speed and high-speed operation, so the bearing input does not increase significantly, and through this, it can be interpreted that the compressor efficiency is improved compared to the past as the bearing input is reduced.

[0118] In addition, in the case where the discharge guide part (1265) is formed on the opposite side of the piston (132) with respect to the second center line (CL2) as in the present embodiment, foreign substances discharged through the discharge guide part (1265) can be prevented from flying toward the compression part (130), that is, between the cylinder (1315) and the piston (132) and / or toward the muffler assembly (142). This prevents foreign substances from flowing between the cylinder (1315) and the piston (132) and causing friction loss and / or wear, and at the same time, prevents foreign substances from flowing into the compression chamber (130a) through the muffler assembly (142).

[0119] In addition, as in the present embodiment, the discharge guide (1265) may correspond to a section in which almost no bearing dynamic pressure is generated, that is, the load direction received by the first end (1261) of the connecting rod (126) in the section described above, that is, the range of 120° to 270° based on the bearing angle of the first end (1261). In other words, the discharge guide (1265) can discharge foreign substances before the bearing dynamic pressure becomes lower than the pressure of the second oil supply groove (1252b) provided in the eccentric pin portion (125c) of the drive shaft (125). Accordingly, foreign substances in the second oil supply groove (1252b) and / or the discharge guide (1265) can be prevented from flowing into the second bearing surface.

[0120] Meanwhile, other examples of the exhaust guide section are as follows.

[0121] That is, in the above-described embodiment, the discharge guide portion is formed to have the same cross-sectional area in the axial direction, but in some cases, the discharge guide portion may be formed to have different cross-sectional areas in the axial direction.

[0122] Fig. 9 is a front view showing a portion of the connecting rod broken off to illustrate another embodiment of the exhaust guide section.

[0123] Referring to FIG. 9, a second oil supply groove (1252b) is formed on the outer surface of the eccentric pin portion (125c) of the drive shaft (125) according to the present embodiment, and an exhaust guide portion (1265) periodically communicating with the second oil supply groove (1252b) may be formed on the inner surface (1261a) of the first end (1261) of the connecting rod (126) facing it. Since the basic configuration and the resulting operational effects of the second oil supply groove (1252b) and the exhaust guide portion (1265) are similar to those of the above-described embodiment, the description thereof will be replaced with the description of the above-described embodiment.

[0124] For example, the second refueling groove (1252b) may be formed so that its upper end is inclined in a forward direction with respect to the rotational direction of the driving shaft (125), and the upper end of the second refueling groove (1252b) may be formed with a height and / or length that is covered by the first end (1261) of the connecting rod (126).

[0125] The discharge guide portion (1265) is formed to be sunken into the inner surface (1261a) of the first end (1261) of the connecting rod (126), and may be formed to overlap the second refueling groove (1252b) in the radial direction. Accordingly, the discharge guide portion (1265) periodically communicates with the second refueling groove (1252b) when the driving shaft (125) rotates, and discharges foreign substances transmitted through the second refueling groove (1252b) into the internal space (110a) of the shell (110).

[0126] In this case, the discharge guide portion (1265) can be formed within a range of 120° to 270° based on the bearing angle received by the first end portion (1261) of the connecting rod (126). Accordingly, foreign substances can be quickly discharged through the discharge guide portion (1265) while suppressing the bearing support capacity from being reduced due to the discharge guide portion (1265).

[0127] However, in the present embodiment, the discharge guide portion (1265) may be formed so that its cross-sectional area expands along the axial direction. For example, the discharge guide portion (1265) may be formed so that the circumferential width (L22) of the open upper end (discharge end) (1265a) is larger than the circumferential width (L21) of the closed lower end. In other words, the discharge guide portion (1265) may be formed with the same depth in the radial direction on the same axis, but may be formed so as to be inclined so that the gap between the two circumferential side surfaces gradually increases as it goes toward the discharge end (1265a). Accordingly, the discharge guide portion (1265) may be formed so that its cross-sectional area increases as it goes from the bottom to the top (discharge end) (1265a). Through this, foreign substances transferred from the second fuel supply groove (1252b) to the discharge guide portion (1265) can be discharged more quickly into the internal space (110a) of the shell (110).

[0128] Although not shown in the drawing, the discharge guide portion (1265) may be formed in multiple stages. For example, the discharge guide portion (1265) may be formed with a first discharge guide portion (not shown) at the bottom and a second discharge guide portion (not shown) at the top in steps. In this case, the circumferential width of the second discharge guide portion may be formed to be larger than the circumferential width of the first discharge guide portion. This allows for easier processing compared to forming the side of the discharge guide portion (1265) at an angle, while also allowing for the rapid discharge of foreign substances.

[0129] Meanwhile, another example of the exhaust guide section is as follows.

[0130] That is, in the embodiments described above, the discharge guide portion is formed along the same axis, but in some cases, the discharge guide portion may be formed to be inclined with respect to the axial direction.

[0131] FIGS. 10a and 10b are front views showing a portion of a connecting rod broken off to illustrate further embodiments of the exhaust guide section.

[0132] Referring to FIGS. 10a and 10b, a second oil supply groove (1252b) is formed on the outer surface of the eccentric pin portion (125c) of the drive shaft (125) according to the present embodiment, and an exhaust guide portion (1265) periodically communicating with the second oil supply groove (1252b) may be formed on the inner surface (1261a) of the first end (1261) of the connecting rod (126) facing it. Since the basic configuration and the resulting operational effects of the second oil supply groove (1252b) and the exhaust guide portion (1265) are similar to those of the above-described embodiment, the description thereof will be replaced with the description of the above-described embodiment.

[0133] For example, the second refueling groove (1252b) may be formed so that its upper end is inclined in a forward direction with respect to the rotational direction of the driving shaft (125), and the upper end of the second refueling groove (1252b) may be formed with a height and / or length that is covered by the first end (1261) of the connecting rod (126).

[0134] The discharge guide portion (1265) is formed to be sunken into the inner surface (1261a) of the first end (1261) of the connecting rod (126), and may be formed to overlap the second refueling groove (1252b) in the radial direction. Accordingly, the discharge guide portion (1265) periodically communicates with the second refueling groove (1252b) when the driving shaft (125) rotates, and discharges foreign substances transmitted through the second refueling groove (1252b) into the internal space (110a) of the shell (110).

[0135] In this case, the discharge guide portion (1265) can be formed within a range of 120° to 270° based on the bearing angle received by the first end portion (1261) of the connecting rod (126). Accordingly, foreign substances can be quickly discharged through the discharge guide portion (1265) while suppressing the bearing support capacity from being reduced due to the discharge guide portion (1265).

[0136] However, in the present embodiment, the discharge guide portion (1265) may be formed to be inclined with respect to the axial direction. For example, as shown in FIG. 10a, the discharge guide portion (1265) may be formed to be inclined in the rotational direction of the driving shaft (125). In other words, the discharge guide portion (1265) may be formed to be inclined from the bottom to the top, but may be formed to be inclined in the forward direction with respect to the rotational direction of the driving shaft (125). Accordingly, the discharge guide portion (1265) may be formed to be inclined in the same direction as the second fuel supply groove (1252b).

[0137] Even in this case, the exhaust guide portion (1265) may be formed to have the same cross-sectional area between both ends, or may be formed to have different cross-sectional areas. This embodiment illustrates an example in which the two ends of the exhaust guide portion (1265) are formed to have the same cross-sectional area.

[0138] In the case where the discharge guide portion (1265) is formed to be inclined in the forward direction with respect to the rotational direction of the drive shaft (125) as described above, foreign substances can be quickly discharged by centrifugal force even if the width of the discharge guide portion (1265) is not formed wide. Accordingly, the width of the discharge guide portion (1265) is reduced, and the surface pressure on the second bearing surface (B2) is reduced accordingly, thereby increasing the bearing's support capacity.

[0139] On the other hand, as shown in FIG. 10b, the discharge guide portion (1265) may be formed to be inclined in the opposite direction to the rotational direction of the driving shaft (125). In other words, the discharge guide portion (1265) may be formed to be inclined from the bottom to the top, but may be formed to be inclined in the opposite direction to the rotational direction of the driving shaft (125). Accordingly, the discharge guide portion (1265) may be formed to be inclined in the opposite direction to the second fuel refueling groove (1252b).

[0140] Even in this case, the exhaust guide portion (1265) may be formed to have the same cross-sectional area between both ends, or may be formed to have different cross-sectional areas. This embodiment illustrates an example in which the two ends of the exhaust guide portion (1265) are formed to have the same cross-sectional area.

[0141] When the discharge guide part (1265) is formed to be inclined in the opposite direction to the rotational direction of the drive shaft (125) as described above, it is possible to minimize foreign substances discharged through the discharge guide part (1265) from flying toward the compression part (130), that is, between the cylinder (1315) and the piston (132), and / or toward the suction muffler (142a). In particular, by suppressing foreign substances from flying toward the compression part (130) during the discharge stroke of the piston (132), it is possible to minimize foreign substances from entering the compression chamber (130a) through the suction passage.

[0142] Meanwhile, another example of the exhaust guide section is as follows.

[0143] That is, in the embodiments described above, the discharge guide part is formed as one discharge end by having one axial end opened, but in some cases, both axial ends of the discharge guide part may be opened to form multiple discharge ends.

[0144] Fig. 11 is a front view showing a portion of a connecting rod broken off to illustrate another embodiment of an exhaust guide section.

[0145] Referring to Fig. 11, a second oil supply groove (1252b) is formed on the outer surface of the eccentric pin portion (125c) of the drive shaft (125) according to the present embodiment, and an exhaust guide portion (1265) periodically communicating with the second oil supply groove (1252b) may be formed on the inner surface (1261a) of the first end (1261) of the connecting rod (126) facing it. Since the basic configuration and the resulting operational effects of the second oil supply groove (1252b) and the exhaust guide portion (1265) are similar to those of the above-described embodiment, the description thereof will be replaced with the description of the above-described embodiment.

[0146] For example, the second refueling groove (1252b) may be formed so that its upper end is inclined in a forward direction with respect to the rotational direction of the driving shaft (125), and the upper end of the second refueling groove (1252b) may be formed with a height and / or length that is covered by the first end (1261) of the connecting rod (126).

[0147] The discharge guide portion (1265) is formed to be sunken into the inner surface (1261a) of the first end (1261) of the connecting rod (126), and may be formed to overlap the second refueling groove (1252b) in the radial direction. Accordingly, the discharge guide portion (1265) periodically communicates with the second refueling groove (1252b) when the driving shaft (125) rotates, and discharges foreign substances transmitted through the second refueling groove (1252b) into the internal space (110a) of the shell (110).

[0148] In this case, the discharge guide portion (1265) can be formed within a range of 120° to 270° based on the bearing angle received by the first end portion (1261) of the connecting rod (126). Accordingly, foreign substances can be quickly discharged through the discharge guide portion (1265) while suppressing the bearing support capacity from being reduced due to the discharge guide portion (1265).

[0149] However, in the present embodiment, the discharge guide (1265) may be formed to penetrate between the axial ends of the inner circumferential surface (1261a) of the first end (1261) of the connecting rod (126). In other words, the upper and lower ends of the discharge guide (1265) may be formed to be opened toward the inner space (110a) of the shell (110), respectively, to have an upper discharge end (1265a1) and a lower discharge end (1265a2). Accordingly, while the discharge guide (1265) is in communication with the second refueling groove (1252b), foreign substances transmitted through the second refueling groove (1252b) can be quickly discharged through both discharge ends (1265a1) (1265a2).

[0150] In this case, the discharge guide part (1265) may be formed so that the cross-sectional area between the two discharge ends (1265a1) (1265a2) is the same, or the cross-sectional area at the two discharge ends (1265a1) (1265a2) may be formed larger than the cross-sectional area at the middle of the discharge guide part (1265). The operational effects of these embodiments are similar to those of the embodiments described above. However, in this embodiment, the cross-sectional areas of the two discharge ends (1265a1) (1265a2) may be formed the same or different. The former is advantageous in terms of processing, and the latter is formed so that the upper discharge end (1265a1) that receives a lot of centrifugal force is larger than the lower discharge end (1265a2), so that foreign substances can be discharged more quickly. In the latter case, on the contrary, the lower side discharge end (1265a2) can be formed larger than the upper side discharge end (1265a1) to increase the amount of foreign substances discharged from the lower side discharge end (1265a2) where the centrifugal force is relatively small.

[0151] Additionally, the discharge guide (1265) may be formed along the same axis, and may be formed to be inclined in a forward or reverse direction with respect to the rotational direction of the drive shaft (125). The operational effects of each of these embodiments are similar to those of the embodiments described above.

[0152] Although not shown in the drawing, the exhaust guide (1265) may be closed at the top and open at the bottom. In this case, the distance of foreign substances flying through the exhaust guide (1265) can be shortened, thereby more effectively suppressing the foreign substances from flowing into the compression unit (130) and / or the muffler assembly (142).

[0153] Meanwhile, another example of the exhaust guide section is as follows.

[0154] That is, in the embodiments described above, the exhaust guide portion is formed as a groove on the inner surface of the first end of the connecting rod, but in some cases, the exhaust guide portion may be formed as a hole.

[0155] Fig. 12 is a front view showing a portion of the connecting rod broken off to illustrate another embodiment of the exhaust guide section.

[0156] Referring to Fig. 12, a second oil supply groove (1252b) is formed on the outer surface of the eccentric pin portion (125c) of the drive shaft (125) according to the present embodiment, and an exhaust guide portion (1265) periodically communicating with the second oil supply groove (1252b) may be formed on the inner surface (1261a) of the first end (1261) of the connecting rod (126) facing it. Since the basic configuration and the resulting operational effects of the second oil supply groove (1252b) and the exhaust guide portion (1265) are similar to those of the above-described embodiment, the description thereof will be replaced with the description of the above-described embodiment.

[0157] For example, the second refueling groove (1252b) may be formed so that its upper end is inclined in a forward direction with respect to the rotational direction of the driving shaft (125), and the upper end of the second refueling groove (1252b) may be formed with a height and / or length that is covered by the first end (1261) of the connecting rod (126).

[0158] The discharge guide (1265) is formed at the first end (1261) of the connecting rod (126), and may be formed to overlap the second refueling groove (1252b) in the radial direction. Accordingly, the discharge guide (1265) periodically communicates with the second refueling groove (1252b) when the driving shaft (125) rotates, and discharges foreign substances transmitted through the second refueling groove (1252b) into the internal space (110a) of the shell (110).

[0159] In this case, the discharge guide portion (1265) can be formed within a range of 120° to 270° based on the bearing angle received by the first end portion (1261) of the connecting rod (126). Accordingly, foreign substances can be quickly discharged through the discharge guide portion (1265) while suppressing the bearing support capacity from being reduced due to the discharge guide portion (1265).

[0160] However, in the present embodiment, the discharge guide portion (1265) may be formed by penetrating from the inner circumference (1261a) to the outer circumference of the first end (1261) of the connecting rod (126). In other words, the discharge guide portion (1265) may penetrate radially through the upper half of the first end (1261) of the connecting rod (126), for example, the upper end of the second oil supply groove (1252b), and may be formed in a circular shape with an inner diameter greater than or equal to the width of the second oil supply groove (1252b). Accordingly, the length of the second oil supply groove (1252b) is sufficiently secured to maintain the amount of oil supplied to the second bearing surface (B2), while foreign substances may be discharged radially through the discharge guide portion (1265). This can reduce the flying distance of foreign substances, thereby preventing foreign substances from entering the compression section (130) and / or the suction / discharge section (140).

[0161] In this case, the discharge guide (1265) may be formed in a long oval shape in the circumferential direction or may be formed in a rectangular shape. In these cases, the time during which the discharge guide (1265) is connected to the second fuel refueling groove (1252b) can be increased, so that foreign substances can be discharged more effectively.

[0162] Although not shown in the drawing, the exhaust guide portion (1265) may be formed to penetrate between the inner surface (1261a) and the outer surface at the top and / or bottom of the first end (1261) of the connecting rod (126). In this case, the exhaust guide portion (1265) can be processed more easily.

Claims

1. Shell in which oil is stored; A driving motor provided in the internal space of the above shell; A drive shaft coupled to the rotor of the above drive motor and having an oil passage to suck up and disperse oil stored in the shell; and The first end is coupled to the drive shaft, and the second end, which forms an end opposite to the first end, includes a connecting rod coupled to a piston to transmit the rotational power of the drive shaft to the piston. A discharge guide part that periodically communicates with the oil passage of the driving shaft is formed at the first end of the above connecting rod. A reciprocating compressor in which the discharge guide section is formed on the opposite side of the piston with respect to the second center line, when the first center line passing through the center of the reciprocating direction of the piston is referred to as the first center line, and the center line perpendicular to the first center line from the center of the first end of the connecting rod is referred to as the second center line.

2. In paragraph 1, The above discharge guide section is, A reciprocating compressor in which the connecting rod is formed within a range of 120° to 270° based on the bearing angle of the first end of the connecting rod at a first position parallel to the first center line.

3. In paragraph 1, The above discharge guide section is, A reciprocating compressor, wherein the first end of the connecting rod is formed within a range of (120° - maximum rotation angle of the first end) to (270° - maximum rotation angle of the first end) based on the bearing angle of the first end of the connecting rod at the second position where the first end of the connecting rod is rotated to the maximum about the first center line centered on the second end of the connecting rod.

4. In paragraph 1, The above discharge guide section is, A reciprocating compressor in which the inner surface of the first end is sunken to a preset depth and a discharge end is formed by opening at least one of the axial ends of the first end.

5. In paragraph 4, The above discharge guide section is, A reciprocating compressor in which the cross-sectional area of ​​the discharge end is formed identical to the cross-sectional area of ​​the side communicating with the oil passage.

6. In paragraph 4, The above discharge guide section is, A reciprocating compressor in which the cross-sectional area of ​​the discharge end is formed larger than the cross-sectional area of ​​the side communicating with the oil passage.

7. In paragraph 4, The above discharge guide section is, A reciprocating compressor extending in the axial direction of the above driving shaft.

8. In paragraph 4, The above discharge guide section is, A reciprocating compressor formed to be inclined in the direction of rotation of the above driving shaft.

9. In paragraph 4, The above discharge guide section is, A reciprocating compressor formed to be inclined in the opposite direction to the rotational direction of the above driving shaft.

10. In paragraph 1, The above discharge guide section is, A reciprocating compressor formed by penetrating from the inner surface to the outer surface of the first end.

11. In paragraph 10, The above discharge guide section is, A reciprocating compressor formed to penetrate the upper half of the first section.

12. In any one of paragraphs 1 to 11, The above driving shaft is provided with an eccentric pin portion into which the first end of the above connecting rod is rotatably inserted, and an oil supply groove forming a part of the oil passage is formed on the outer surface of the eccentric pin portion. The above refueling home is, A reciprocating compressor formed lower than or equal to the axial upper end of the first end.

13. In paragraph 12, The circumferential width of the above discharge guide section is A reciprocating compressor formed to have a circumferential width greater than or equal to that of the above-mentioned fuel receptacle.

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