Reciprocating compressor

Abstract

A reciprocating compressor is disclosed. The reciprocating compressor comprises a shell, an electric motor part, a compression part, a crankshaft, and a balance weight, wherein the balance weight may be provided with a scattering guide part that extends from a fixing part in a direction facing away from an eccentric mass part and guides oil scattered from an oil flow path toward the compression part. Accordingly, a large quantity of oil from the oil scattered from the oil flow path is scattered farther toward a cylinder and a piston and smoothly supplied between the inner circumferential surface of the cylinder and the outer circumferential surface of the piston, thereby improving cooling capacity and / or energy efficiency of the compressor.

Description

Reciprocating compressor

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

[0002] A reciprocating compressor draws in, compresses, and discharges refrigerant as a piston reciprocates within a cylinder. Reciprocating compressors can be classified into connected reciprocating compressors and vibrating reciprocating compressors depending on the piston's driving method.

[0003] A connected-type reciprocating compressor is a method in which a piston connected to a rotary motor via a crankshaft and a connecting rod reciprocates within a cylinder, and a vibrating-type reciprocating compressor is a method in which a piston connected to the actuator of a reciprocating motor reciprocates within a cylinder. The present invention relates to a connected-type reciprocating compressor, and hereinafter, a reciprocating compressor may be understood as a connected-type reciprocating compressor.

[0004] In the case of the reciprocating compressor described above, oil drawn in through the crankshaft is sprayed from the top and / or near the top of the crankshaft and supplied between the cylinder and the piston.

[0005] However, as described above, in reciprocating compressors, there may be cases where oil splashed from the top and / or near the top of the crankshaft is not sufficiently supplied between the cylinder and the piston. In particular, when the reciprocating compressor operates at low speeds, the distance of the oil splashing shortens drastically, which may prevent the oil from reaching the cylinder and piston sufficiently. Consequently, the cylinder, which generates heat during the compression process, cannot be sufficiently cooled, which may lead to a decrease in compression efficiency.

[0006] Considering this, a separate oil supply device, such as an oil guide cap, can be added to the top of the crankshaft; however, this may not only increase costs due to the addition of a separate oil supply device but also reduce reliability regarding the detachment of the device.

[0007] The objective of the present invention is to provide a reciprocating compressor capable of smoothly supplying oil between the cylinder and the piston, not only during high-speed operation but also during low-speed operation.

[0008] Another objective of the present invention is to provide a reciprocating compressor that can smoothly supply oil between the cylinder and the piston regardless of the operating speed by extending the splash distance of oil splashed from the crankshaft.

[0009] Another objective of the present invention is to provide a reciprocating compressor capable of increasing the oil splash distance without adding separate components.

[0010] To achieve the objective of the present invention, a reciprocating compressor comprising a shell, a drive unit, a compression unit, a crankshaft, and a balance weight may be provided. The shell may store a predetermined amount of oil. The drive unit is provided inside the shell and may provide a driving force. The compression unit may compress a refrigerant as a piston reciprocates inside a cylinder by means of the driving force of the drive unit. The crankshaft may be provided with an eccentric portion eccentric with respect to a rotational center and may have an oil passage so that the oil stored in the shell is drawn toward the eccentric portion. The balance weight may be coupled to the eccentric portion of the crankshaft and may rotate together with the crankshaft. The balance weight may include a fixed portion, an eccentric mass portion, and a scattering guide portion. The fixed portion may be coupled to the eccentric portion of the crankshaft. The eccentric mass portion may extend radially and eccentrically from the fixed portion. The above-mentioned scattering guide extends from the above-mentioned fixed part in a direction facing away from the above-mentioned eccentric mass part, thereby guiding the oil scattered from the above-mentioned oil passage toward the above-mentioned compression part. Through this, a large amount of oil scattered from the oil passage is scattered further toward the cylinder and piston, and is smoothly supplied between the inner surface of the cylinder and the outer surface of the piston, thereby improving the cooling power and / or energy efficiency of the compressor.

[0011] For example, the scatter guide may be formed such that at least a portion thereof is located on a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. Through this, even if the scatter guide extends radially from one side of the circumferential direction of the eccentric mass, the center of gravity of the balance weight is located on the virtual line, thereby effectively offsetting the eccentric load caused by the eccentric part of the crankshaft.

[0012] For example, the scatter guide may be formed so that both sides in the circumferential direction are symmetrical with respect to the virtual line. Through this, even if the scatter guide extends radially from one side in the circumferential direction of the eccentric mass, the eccentric load caused by the eccentric part of the crankshaft can be effectively offset.

[0013] Alternatively, the above-mentioned scatter guide may be formed asymmetrically so as to be eccentrically opposite to the rotational direction of the crankshaft with respect to the above-mentioned virtual line. Through this, a large amount of oil scattered from the oil scatter hole can be smoothly guided toward the cylinder and piston while minimizing the area of ​​the scatter guide.

[0014] As another example, the above-mentioned scatter guide may be formed eccentrically to one side in the circumferential direction with respect to a virtual line passing through the center of gravity of the above-mentioned eccentric mass and the center of the eccentric part of the crankshaft. Through this, a large amount of oil scattered from the oil scatter hole can be smoothly guided toward the cylinder and piston while minimizing the area of ​​the scatter guide.

[0015] For example, the above-mentioned scatter guide may be formed on the side opposite to the rotational direction of the crankshaft. Through this, a large amount of oil scattered from the oil scatter hole can be smoothly guided toward the cylinder and piston while minimizing the surface area of ​​the scatter guide, even during low-speed operation as well as high-speed operation.

[0016] As another example, the above-mentioned scatter guide may be formed such that its circumferential length is greater than or equal to its radial length. Through this, a large amount of oil scattered from the oil scatter hole can be smoothly guided between the cylinder and the piston while minimizing the radial length of the scatter guide.

[0017] As another example, the scatter guide may be formed such that its circumferential length is less than or equal to its radial length. Through this, the radial length of the scatter guide can be formed to be as long as possible, thereby further increasing the scatter distance.

[0018] As another example, the scatter guide may be formed such that the gap between the two circumferential sides narrows as it moves away from the fixed part. Through this, the radial length of the scatter guide is formed as long as possible while minimizing the area of ​​the scatter guide, thereby allowing a large amount of oil scattered from the oil scatter hole to be smoothly guided between the cylinder and the piston.

[0019] As another example, at least a portion of the gap between the two circumferential sides of the scatter guide may be formed uniformly along the radial direction. This allows the scattering distance and / or amount of oil to be increased while maintaining a small radial length of the scatter guide.

[0020] As another example, the distance between the center of the eccentric part and the end of the scatter guide part may be formed to be smaller than the value obtained by subtracting the eccentricity of the eccentric part from the shortest distance between the end of the cylinder and the eccentric mass part when the piston is in the top dead center position. Through this, the scatter guide part of the balance weight can be prevented from colliding with the cylinder when the balance weight rotates.

[0021] As another example, an oil splash hole may be formed in the crankshaft, extending from the oil passage and penetrating the outer surface of the eccentric portion. The circumferential length of the splash guide may be formed to be greater than or equal to the inner diameter of the oil splash hole. Through this, the circumferential length of the splash guide is appropriately set according to the size of the oil splash hole, so that the oil splashed from the oil splash hole can be smoothly guided between the cylinder and the piston.

[0022] As another example, an oil splash hole may be formed in the crankshaft, extending from the oil passage and penetrating the outer surface of the eccentric part. The gap between the top of the eccentric part and the upper surface of the splash guide may be formed to be greater than or equal to the gap between the top of the eccentric part and the center of the oil splash hole. Through this, the assemblability and / or reliability of the balance weight are improved, while the splash guide of the balance weight is not located too far from the bottom of the oil splash hole, thereby allowing oil to be smoothly guided between the cylinder and the piston.

[0023] For example, the upper surface of the scattering guide may be provided at the same height as the lower end of the oil scattering hole. By doing so, the axial falling of oil discharged through the oil scattering hole can be minimized, thereby further increasing the oil scattering distance.

[0024] Additionally, the upper surface of the above-mentioned scatter guide is positioned lower than the lower surface of the above-mentioned oil scatter hole, and the gap between the lower surface of the above-mentioned oil scatter hole and the upper surface of the scatter guide may be formed to be smaller than or equal to the inner diameter of the above-mentioned oil scatter hole. Through this, the assemblability and / or reliability of the balance weight are improved, while the scatter guide of the balance weight is not located too far from the lower surface of the oil scatter hole, thereby allowing oil to be smoothly guided between the cylinder and the piston.

[0025] As another example, the oil passage may be formed by penetrating through the upper end of the eccentric part. The gap between the upper end of the eccentric part and the upper surface of the scatter guide may be formed to be smaller than or equal to the inner diameter of the oil passage at the upper end of the eccentric part. Through this, oil can be smoothly supplied between the cylinder and the piston while easily machining the crankshaft including the oil passage.

[0026] As another example, the scatter guide can be formed with the same thickness as the fixed part. This facilitates the processing of the scatter guide.

[0027] As another example, the scatter guide may be formed thinner than the fixed portion. This reduces the weight of the scatter guide, thereby increasing its circumferential length and / or radial length to increase the amount of lubrication between the cylinder and the piston.

[0028] As another example, the upper surface of the scattering guide may be formed flush with the upper surface of the fixed part. This allows the scattering guide to be easily machined while guiding the oil discharged through the oil scattering hole to scatter far toward the cylinder.

[0029] As another example, the scatter guide may be formed such that its upper surface is inclined or curved so that it becomes axially higher from the inner side to the outer side of the scatter guide. Through this, the scatter guiding effect can be further enhanced under conditions where the circumferential length and / or radial length of the scatter guide are the same.

[0030] As another example, the scatter guide may be formed within a range of ±45 degrees on both sides in the circumferential direction, based on a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. By doing so, the scatter guide may be prevented from being formed excessively wide in the circumferential direction, thereby preventing a reduction in the eccentric load offsetting effect of the eccentric mass caused by the scatter guide even if the scatter guide is formed on the opposite side of the eccentric mass.

[0031] For example, the scatter guide may be formed in a portion of the above range. Through this, while forming the scatter guide, the reduction of the eccentric load offsetting effect of the eccentric mass part according to the scatter guide is suppressed, and at the same time, the increase in weight of the balance weight is minimized, thereby suppressing the decrease in motor efficiency.

[0032] In addition, the above-mentioned scatter guide can be formed over the entire length of the above range. By doing so, the area of ​​the scatter guide can be formed as wide as possible, thereby allowing a large amount of oil scattered from the oil scatter hole to be guided more smoothly between the cylinder and the piston.

[0033] In addition, to achieve the objective of the present invention, a reciprocating compressor comprising a shell, a drive unit, a compression unit, a crankshaft, and a balance weight may be provided. The shell may store a predetermined amount of oil. The drive unit is provided inside the shell and may provide driving force. The compression unit may compress the refrigerant as a piston reciprocates inside a cylinder by means of the driving force of the drive unit. The crankshaft may be provided with an eccentric portion eccentric with respect to the center of rotation and may be provided with an oil passage so that the oil stored in the shell is drawn toward the eccentric portion. The balance weight may be coupled to the eccentric portion of the crankshaft and may rotate together with the crankshaft. An oil splash hole is formed on the outer surface of the eccentric portion through which one end of the oil passage passes, and the balance weight may be provided with a fixing portion to surround and be coupled to the eccentric portion of the crankshaft. The fixing portion may be coupled at a position where the gap between the upper surface of the fixing portion and the center of the oil splash hole is smaller than or equal to the inner diameter of the oil splash hole. Through this, the oil discharged through the oil splash hole travels along the fixed part of the balance weight and splashes far toward the cylinder, facilitating the smooth supply of oil between the cylinder and the piston.

[0034] For example, the upper surface of the fixed part may be connected at the same height as the lower end of the oil splash hole. By doing so, the oil discharged through the oil splash hole may fall axially, thereby further increasing the oil splash distance.

[0035] As another example, the upper surface of the fixed part may be formed to form a flat plane along the radial direction. This allows the fixed part to be easily machined while guiding the oil discharged through the oil splash hole to splash far toward the cylinder.

[0036] As another example, the upper surface of the fixed part may be formed such that the axial height increases from the inner circumference to the outer circumference of the fixed part. Through this, the scattering guidance effect can be further enhanced under conditions where the radial length of the fixed part is the same.

[0037] As another example, the balance weight may further include a scatter guide extending radially from the outer surface of the fixed part to guide the oil scattered from the oil passage toward the compression part. Through this, a large amount of oil discharged through the oil passage is scattered further toward the cylinder and piston, and is smoothly supplied between the inner surface of the cylinder and the outer surface of the piston, thereby improving the cooling power and / or energy efficiency of the compressor.

[0038] The reciprocating compressor of the present invention comprises a shell, a transmission unit, a compression unit, a crankshaft, and a balance weight, wherein the balance weight may be provided with a scatter guide extending from a fixed part in a direction facing away from an eccentric mass part to guide oil scattered from an oil passage toward the compression unit. Through this, a large amount of oil scattered from the oil passage is scattered further toward the cylinder and piston, and is smoothly supplied between the inner surface of the cylinder and the outer surface of the piston, thereby improving the cooling power and / or energy efficiency of the compressor.

[0039] The reciprocating compressor of the present invention may be formed such that at least a portion of the scatter guide is located on a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. Through this, even if the scatter guide extends radially from one side of the circumferential direction of the eccentric mass, the center of gravity of the balance weight is located on the virtual line, thereby effectively offsetting the eccentric load caused by the eccentric part of the crankshaft.

[0040] The reciprocating compressor of the present invention may be formed eccentrically such that the scatter guide is spaced circumferentially to one side with respect to a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. Through this, a large amount of oil scattered from the oil scatter hole can be smoothly guided toward the cylinder and piston while minimizing the area of ​​the scatter guide.

[0041] In the reciprocating compressor of the present invention, the upper surface of the scattering guide can be formed flush with the upper surface of the fixed part. Through this, the scattering guide can be easily machined while guiding the oil discharged through the oil scattering hole to scatter far toward the cylinder.

[0042] In the reciprocating compressor of the present invention, the upper surface of the scatter guide section may be formed to be inclined or curved so that it becomes axially higher from the inner side to the outer side of the scatter guide section. Through this, the scatter guiding effect can be further enhanced under conditions where the circumferential length and / or radial length of the scatter guide section are the same.

[0043] In the reciprocating compressor of the present invention, the scatter guide can be formed within a range of ±45 degrees on both sides in the circumferential direction based on a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft. By doing so, the scatter guide is prevented from being formed excessively wide in the circumferential direction, thereby preventing a reduction in the eccentric load offsetting effect of the eccentric mass caused by the scatter guide even if the scatter guide is formed on the opposite side of the eccentric mass.

[0044] The reciprocating compressor of the present invention comprises a shell, a transmission unit, a compression unit, a crankshaft, and a balance weight, wherein the fixed portion of the balance weight may be coupled at a position where the gap between the upper surface of the fixed portion and the center of the oil splash hole is smaller than or equal to the inner diameter of the oil splash hole. Through this, oil discharged through the oil splash hole can travel along the fixed portion of the balance weight and splash far toward the cylinder, thereby facilitating the smooth supply of oil between the cylinder and the piston.

[0045] FIG. 1 is a perspective view showing the interior of a shell of a reciprocating compressor according to the present embodiment after disassembly.

[0046] FIG. 2 is a cross-sectional view showing the interior of a reciprocating compressor according to FIG. 1.

[0047] FIG. 3 is a perspective view showing the balance weight according to the present embodiment disassembled from the crankshaft.

[0048] FIG. 4 is a perspective view showing the balance weight assembled on the crankshaft in FIG. 3.

[0049] Fig. 5 is a plan view of Fig. 4.

[0050] FIG. 6 is a cross-sectional view along "VI-VI" of FIG. 5.

[0051] FIG. 7 is a plan view showing a balance weight equipped with a scattering guide of the present embodiment.

[0052] FIGS. 8A and 8B are schematic diagrams showing the simulated scattering distance by driving speed according to the presence or absence of a scattering guide.

[0053] Figures 9a and 9b are graphs showing a comparison of cooling power and energy efficiency by operating speed with and without a scatter guide.

[0054] FIG. 10 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0055] FIG. 11 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0056] FIG. 12 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0057] FIGS. 13 and FIGS. 14 are plan views showing a balance weight equipped with a scatter guide section of another embodiment.

[0058] FIG. 15 is a cross-sectional view showing a balance weight equipped with a scatter guide section of another embodiment.

[0059] FIG. 16 is a cross-sectional view showing another embodiment regarding the assembly position of the balance weight according to the present embodiment.

[0060] FIG. 17 is a cross-sectional view showing another embodiment of the assembly position of the balance weight according to the present embodiment.

[0061] Hereinafter, a reciprocating compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings. In this specification, identical or similar reference numbers are assigned to identical or similar components even in different embodiments, and the description thereof is replaced by the first description.

[0062] Singular expressions used in this specification may include plural expressions unless the context clearly indicates otherwise. Additionally, in describing the embodiments disclosed in this specification, detailed descriptions of related prior art are omitted if it is determined that such detailed descriptions could obscure the essence of the embodiments disclosed in this specification.

[0063] In addition, it should be noted that the attached drawings are intended only to facilitate understanding of the embodiments disclosed in this specification, and should not be interpreted as limiting the technical ideas disclosed in this specification by the attached drawings.

[0064] In addition, the following description defines the compression chamber side as the front and the opposite side as the rear relative to the piston, and defines the lower shell side as the axial downward and the upper shell side as the axial upward relative to the crankshaft.

[0065] FIG. 1 is a perspective view showing the interior of a shell of a reciprocating compressor according to the present embodiment after disassembly, and FIG. 2 is a cross-sectional view showing the interior of a reciprocating compressor according to FIG. 1.

[0066] Referring to FIGS. 1 and 2, the reciprocating compressor according to the present embodiment may include a shell (110) forming an exterior, an electric motor (120) provided in the internal space (110a) of the shell (110) and providing driving force, a compression unit (130) that receives driving force from the electric motor (120) and compresses a refrigerant, and a suction / discharge unit (140) that guides the refrigerant to a compression chamber (130a) and discharges the compressed refrigerant.

[0067] 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 driving unit (120) and a compression unit (130). The shell (110) may be made of a lightweight aluminum alloy with a high thermal conductivity (hereinafter abbreviated as aluminum).

[0068] The lower shell (111) may be formed in a roughly hemispherical shape. A suction pipe (115), a discharge pipe (116), and a process pipe (not shown) may each be connected to the lower shell (111) by penetrating through it. These suction pipe (115), discharge pipe (116), and process pipe may each be connected to the lower shell (111) by an insert die-casting method.

[0069] The upper shell (112) can be formed in a roughly hemispherical shape, similar to the lower shell (111). The upper shell (112) can be coupled 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.

[0070] Referring to FIGS. 1 and 2, the electric motor (or drive motor) (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) is elastically supported against the internal 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).

[0071] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0072] The stator core (1211) is made of a metal material such as electrical steel, and when voltage is applied from the outside to the motor unit (120), it performs electromagnetic interaction through electromagnetic force together with the stator coil (1212) and rotor (122) to be described later.

[0073] The stator core (1211) is formed in a roughly rectangular shape. For example, the inner surface of the stator core (1211) may be formed in a circular shape, and the outer surface may be formed in a rectangular shape. The stator core (1211) may be fixed to the lower surface of the cylinder block (131) described later by a stator fastening bolt (not shown).

[0074] The stator core (1211) can be elastically supported by a support spring (123) on the bottom surface of the shell (110) while being spaced axially and radially apart from the inner surface of the shell (110). Accordingly, vibrations generated during operation can be suppressed from being directly transmitted to the shell (110).

[0075] The stator coil (1212) can be wound inside the stator core (1211). As previously described, when voltage is applied from the outside, the stator coil (1212) generates an electromagnetic force and performs electromagnetic interaction with the stator core (1211) and the rotor (122). Through this, the motor unit (120) generates a driving force for the reciprocating motion of the compression unit (130).

[0076] The rotor (122) may include a rotor core (1221) and a magnet (1222).

[0077] The rotor core (1221), like the stator core (1211), is made of a metal material such as electrical steel and can be formed in a roughly cylindrical shape. A crank shaft (125), which will be described later, can be press-fitted and connected to the center of the rotor core (1221).

[0078] The magnet (1222) is made of a permanent magnet and can be inserted and coupled at equal intervals along the circumferential direction of the rotor core (1221). When voltage is applied, the rotor (122) rotates through electromagnetic interaction with the stator core (1211) and the stator coil (1212). Accordingly, the crank shaft (125) rotates together with the rotor (122) and transmits the rotational force of the electric motor (120) to the compression unit (130) through the connecting rod (126).

[0079] The crankshaft (125) according to the present embodiment may include a shaft portion (1251), a bearing portion (1252), a plate portion (1253), and an eccentric portion (1254).

[0080] The shaft portion (1251) is a part that is pressed into the rotor core (1221), and a first oil passage (1255a) that forms part of the oil passage (1255) may be formed inside the shaft portion (1251). The first oil passage (1255a) is formed by penetrating through the bottom of the shaft portion (1251), and an oil feeder (1256) may be provided at the bottom of the first oil passage (1255a). Accordingly, the oil feeder (1256) rotates together with the shaft portion (1251) and pumps oil stored in the lower half of the shell (110), and this oil is guided through the first oil passage (1255a) to the second oil passage (1255b) provided on the outer surface of the bearing portion (1252).

[0081] The bearing portion (1252) is a part provided in the middle of the crankshaft (125), that is, between the shaft portion (1251) and the eccentric portion (1254), and is rotatably inserted into the bearing portion (1313) of the cylinder block (131) to be described later.

[0082] The plate portion (1253) extends radially to form a flange shape at the top of the bearing portion (1252) and can be rotatably supported on the upper surface of the bearing portion (1313) of the cylinder block (310) described later. A bearing member (not shown), such as a ball bearing, may be provided between the plate portion (1253) and the bearing portion (1313) facing it. Accordingly, the crankshaft (125) can be axially supported on the cylinder block (131).

[0083] The eccentric portion (1254) may be formed by extending axially from the upper surface of the plate portion (1253). The eccentric portion (1254) is formed eccentrically with respect to the rotational center of the crankshaft (125) (or the rotational center of the shaft portion) (Oc), so that the connecting rod (126), which will be described later, can be rotatably inserted. Accordingly, when the crankshaft (125) rotates, the connecting rod (126) performs linear reciprocating motion in the forward and backward directions, thereby converting the rotational motion of the crankshaft (125) into the linear reciprocating motion of the piston (132).

[0084] Additionally, a third oil passage (1255c), which communicates with the second oil passage (1255b) and forms another part of the oil passage (1255), is formed by penetrating the upper end of the eccentric part (1254), and an oil scattering hole (1255d), which forms the outlet of the oil passage (1255), can be formed by penetrating radially to the outer surface of the eccentric part (1254) at the middle height of the eccentric part (1254). Accordingly, oil sucked up to the eccentric part (1254) is scattered from the third oil passage (1255c) and / or the oil scattering hole (1255d) to cool the electric motor (120) and the compression part (130), while simultaneously lubricating the cylinder (1314) and the piston (132) forming the compression part (130).

[0085] Additionally, a balance weight (127) that offsets the eccentric load may be attached to the eccentric part (1254). For example, the balance weight (127) may be pressed into the outer surface of the eccentric part (1254) and integrally attached. Accordingly, the balance weight (127) offsets the eccentric load while rotating together with the eccentric part (1254) in an eccentric state with respect to the rotation center (Oc) of the crank shaft (125). The balance weight (127) will be explained again later.

[0086] Referring to FIGS. 1 and 2, 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 by a shell (110), and the piston (132) is coupled to a crankshaft (125) by a connecting rod (126) and moves relative to the cylinder block (131).

[0087] 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) may be connected to the stator (121) by a stator-fastening bolt (not shown) and elastically supported on the lower shell (111) together with the stator (121) of the electric motor (120).

[0088] The cylinder block (131) may include a frame portion (1311), a fixed protrusion (1312), a bearing portion (1313), and a cylinder portion (hereinafter abbreviated as cylinder) (1314). The frame portion (1311) is a part that forms the main body of the cylinder block (131), the fixed protrusion (1312) is a part that is coupled to the stator (121) of the electric motor (120), the bearing portion (1313) is a part that supports the crankshaft (125), and the cylinder (1314) is a part into which the piston (132) is slidably inserted to form a compression space (V).

[0089] The frame portion (1311) may be formed in a flat plate shape extending in the transverse direction, or may be formed in a radiating plate shape by reducing the thickness of a portion of the edge excluding the corners. Accordingly, the frame portion (1311) is provided on the upper side of the electric motor portion (120) so that the electric motor portion (120) and the compression portion (130) can be separated.

[0090] The fixed protrusion (1312) may be formed on 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 electric motor portion (120). Accordingly, the cylinder block (131) can be bolted to the stator (121) and elastically supported on the lower shell (111) together with the stator (121) of the electric motor portion (120).

[0091] The bearing portion (1313) may be formed by extending axially in both directions from the central part of the frame portion (1311). A bearing hole (1313a) may be formed axially through the bearing portion (1313) so that the crankshaft (125) passes through it. Accordingly, the shaft portion (1251) of the crankshaft (125) is inserted into the bearing portion (1313) and supported radially, while the plate portion (1253) of the crankshaft (125) is placed on the top of the bearing portion (1313) and supported axially.

[0092] The cylinder (1314) may be formed radially eccentrically at one edge of the frame portion (1311). The cylinder (1314) is radially perforated so that a piston (132) connected to a connecting rod (126) is inserted into the inner opening, and a valve assembly (141) forming the suction / discharge portion (140) to be described later may be mounted at the outer opening. Accordingly, the piston (132) may be inserted into the interior of the cylinder (1314) to perform linear reciprocating motion, thereby forming a compression chamber (130a).

[0093] According to the present embodiment, the piston (132) may be formed with an open side (rear side) facing the connecting rod (126), while the opposite side, the front side facing away from the connecting rod (126), may be formed in a closed shape. 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) is formed in a closed shape to form a compression chamber (130a) inside the cylinder (1314) together with the valve assembly (141) to be described later.

[0094] Additionally, the piston (132) may be formed from the same material as the cylinder block (131), for example, an aluminum alloy. Accordingly, the transmission of magnetic flux from the rotor (122) to the piston (132) is suppressed, and at the same time, the thermal expansion coefficients of the cylinder block (specifically the cylinder) (131) and the piston (132) are the same, thereby suppressing interference caused by thermal expansion between the cylinder block (131) and the piston (132).

[0095] The suction and discharge unit (140) according to the present embodiment may include a valve assembly (141), a suction muffler (142), and a discharge muffler (143). The valve assembly (141) is a member that opens and closes the compression chamber (130a) of the cylinder block (131), the suction muffler (142) is a member that reduces the suction noise of the refrigerant sucked into the compression chamber (130a), and the discharge muffler (143) is a member that reduces the discharge noise of the refrigerant discharged from the compression chamber (130a).

[0096] The valve assembly (141) may be equipped with an intake valve (not shown) and a discharge valve (not shown) and may be coupled to the end of the cylinder block (131). The intake valve and the discharge valve may be provided separately, but they may typically be formed together on the same valve plate. The intake valve may be formed to open and close in the direction toward the piston (132), while the discharge valve may be formed to open and close in the opposite direction to the intake valve. Accordingly, the intake valve may not be provided with a separate retainer, whereas the discharge valve may be provided with a retainer that limits the opening amount of the discharge valve.

[0097] The intake muffler (142) is provided with an intake space in which the inlet is indirectly connected to the intake pipe (115), and the outlet of the intake space can be directly connected to the intake side of the valve assembly (141). Accordingly, the refrigerant can be sucked into the compression chamber (130a) of the cylinder (1314) while passing through the intake space of the intake muffler (142) with the intake noise attenuated.

[0098] The discharge muffler (143) is provided with a discharge space in which the inlet is connected to the discharge side of the valve assembly (141), and the outlet of the discharge space can be directly connected to the discharge pipe (116) through the loop pipe (117). Accordingly, a low-pressure compressor can be formed in which the refrigerant compressed in the compression chamber (130a) is discharged directly to the outside of the compressor through the loop pipe (118) and the discharge pipe (116) without passing through the internal space (110a) of the shell (110).

[0099] The reciprocating compressor according to the present embodiment as described above operates as follows.

[0100] That is, when power is applied to the electric motor (120), the rotor (122) rotates. When the rotor (122) rotates, the crankshaft (125) connected to the rotor (122) rotates and transmits rotational force to the piston (132) through the connecting rod (126). The piston (132) reciprocates in the forward and backward directions relative to the cylinder (1314) by means of the connecting rod (126).

[0101] For example, when the piston (132) moves backward (intake stroke) in the cylinder (1314), the volume of the compression chamber (130a) increases, and the refrigerant is drawn into the compression chamber (130a) through the intake pipe (115) and intake muffler (142). When the piston (132) moves forward (discharge stroke) in the cylinder (1314), the volume of the compression chamber (130a) decreases, and the refrigerant filled in the compression chamber (130a) is compressed and discharged into the refrigeration cycle through the discharge muffler (143), loop pipe (118), and discharge pipe (116), repeating a series of processes.

[0102] At this time, the oil stored in the internal space (110a) of the shell (110) is drawn up along the first oil passage (1255a) of the crankshaft (125) and is scattered through the third oil passage (1255c) opened at the upper half of the crankshaft (125), that is, the top of the eccentric part (1254), and / or through the oil scattering hole (1255d) opened at the outer surface of the eccentric part (1254). A portion of this oil cools the transmission part (120), while another portion of the oil is supplied between the inner surface of the cylinder (1314) forming the compression part (130) and the outer surface of the piston (132) to cool and / or lubricate the space between the cylinder (1314) and the piston (132).

[0103] However, conventionally, oil sprayed from the third oil passage (1255c) and / or oil spray hole (1255d) may not reach the cylinder (1314) and / or piston (132) smoothly, and thus a decrease in cooling power may occur due to friction loss caused by a lack of oil and / or refrigerant leakage between the inner surface of the cylinder (1314) and the outer surface of the piston (132). This may occur more significantly when the compression volume increases, thereby increasing the contact area between the cylinder (1314) and the piston (132).

[0104] Accordingly, in this embodiment, a scatter guide portion (1273) extending toward the cylinder (1314) may be formed on the balance weight (127), or the balance weight (127) may be positioned adjacent to the oil scatter hole (1255d) without forming a separate scatter guide portion on the balance weight (127). Through this, a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be scattered further away from the oil scatter hole (1255d) toward the cylinder (1314) and the piston (132), and smoothly supplied between the inner surface of the cylinder (1314) and the outer surface of the piston (132).

[0105] FIG. 3 is a perspective view showing a balance weight according to the present embodiment disassembled from a crankshaft, FIG. 4 is a perspective view showing the balance weight in FIG. 3 assembled to a crankshaft, FIG. 5 is a plan view of FIG. 4, FIG. 6 is a cross-sectional view taken along line "VI-VI" of FIG. 5, and FIG. 7 is a plan view showing a balance weight equipped with a scatter guide portion according to the present embodiment.

[0106] Referring to FIGS. 3 to 5, the balance weight (127) according to the present embodiment may include a fixed part (1271), an eccentric mass part (1272), and a scatter guide part (1273). The fixed part (1271) is a part coupled to the crankshaft (125), the eccentric mass part (1272) is a part that offsets the eccentric load caused by the eccentric part (1254) of the crankshaft (125), and the scatter guide part (1273) is a part that scatters a large amount of oil from the oil scatter hole (1255d) of the crankshaft (125) further toward the cylinder (1314) and piston (132).

[0107] The fixed portion (1271) may be formed in an annular shape. For example, the fixed portion (1271) may have a fixing hole (1271a) penetrating its center. Accordingly, the fixed portion (1271) may be inserted into and fixed to the eccentric portion (1254) of the crankshaft (125).

[0108] In this case, the fixed portion (1271) may be formed with the same or nearly the same thickness and width along the circumferential direction. Accordingly, the fixed portion (1271) exerts the same or nearly the same bonding force along the circumferential direction, so that the balance weight (127) can be stably bonded to the crank shaft (125). In this embodiment, an example is illustrated in which the radial width of the fixed portion (1271) is formed to be nearly the same. In other words, the radial width of the fixed portion (1271) in this embodiment may be formed to be somewhat narrower on the opposite side of the eccentric mass portion (1272). However, below, the radial width of the fixed portion (1271) may be defined and described as being the same.

[0109] Although not illustrated in the drawing, the fixed portion (1271) may be formed with different widths and thicknesses along the circumferential direction. For example, the width and / or thickness of the fixed portion (1271) at the side far from the eccentric mass portion (1272) may be formed to be relatively smaller than the width and / or thickness of the fixed portion (1271) at the side near the eccentric mass portion (1272). In this case, the fixed portion (1271) may form a part of the eccentric mass portion (1272) together with the eccentric mass portion (1272). Conversely, it may be formed in the opposite way to improve the reliability of the fixed portion (1271).

[0110] In addition, in this case, at least one fixing projection (1271c) may be formed on the inner surface of the fixing part (1271). For example, a plurality of fixing projections (1271c) may each be formed protruding radially on the inner surface of the fixing hole (1271a). Accordingly, the radial width of the fixing part (1271) including the fixing projections (1271c) may be formed differently along the circumferential direction. In other words, the radial width of the fixing part (1271) may be wide in the part where the fixing projections (1271c) are present and narrow in the part where the fixing projections (1271c) are not present. However, it may be understood that the radial width of the fixing part (1271) is defined excluding the fixing projections (1271c) below.

[0111] Referring to FIG. 6, the fixed part (1271) according to the present embodiment may be coupled to a lower side than the oil splash hole (1255d). For example, the fixed part (1271) may be coupled to the eccentric part (1254) such that the upper surface (1271b) of the fixed part (1271) facing away from the electric part (120) is lower than the lower end of the oil splash hole (1255d), for example, so that the upper surface (1271b) of the fixed part (1271) is positioned radially in alignment with the lower end (P2) of the oil splash hole (1255d). In other words, the fixed part (1271) may be coupled to the eccentric part (1254) such that the upper surface (1273a) of the splash guide part (1273) is positioned at the same height as the lower end (P2) of the oil splash hole (1255d). Accordingly, the fixed part (1271) does not overlap radially with the oil scattering hole (1255d), so that oil sucked in through the oil passage (1255) can be smoothly scattered through the oil scattering hole (1255d).

[0112] The eccentric mass portion (1272) may extend radially from one side of the outer surface of the fixed portion (1271). For example, the eccentric mass portion (1272) may be formed eccentrically with respect to the fixed portion (1271) with respect to the rotation center (Oc) of the crankshaft (125), that is, eccentrically in the opposite direction to the eccentric portion (1254). Accordingly, the eccentric mass portion (1272) can generate an eccentric load by centrifugal force when the crankshaft (125) rotates, thereby offsetting the eccentric load caused by the eccentric portion (1254) of the crankshaft (125).

[0113] The eccentric mass portion (1272) is formed in a semicircular shape, but may be formed thicker than the thickness of the fixed portion (1271). For example, the eccentric mass portion (1272) may be formed into a single bundle shape by forging, welding or fastening multiple mass portions, or by folding multiple mass portions so that they can be folded. The former can improve the reliability of the eccentric mass portion (1272), and the latter can facilitate weight control of the eccentric mass portion (1272). This embodiment is described using the former as an example.

[0114] Referring to FIGS. 5 to 7, the scatter guide (1273) according to the present embodiment may be extended radially from the outer circumference of the other side of the fixed part (1271). For example, the scatter guide (1273) may be formed by extending toward the piston (132) at a position higher than the highest point of the piston (132) in a direction facing away from the eccentric mass part (1272). Accordingly, a large amount of oil among the oil scattered through the oil scatter hole (1255d) may be scattered further along the scatter guide (1273), thereby increasing the amount of oil supplied between the cylinder (1314) and the piston (132).

[0115] Specifically, the scatter guide section (1273) according to the present embodiment may be positioned so as not to be higher than the oil scatter hole (1255d). In other words, the scatter guide section (1273) may be formed at a position where the gap (G1) between the upper surface (1273a) of the scatter guide section (1273) and the upper end (1254a) of the eccentric section (1254) is greater than or equal to the gap (G2) between the center (Oh) of the oil scatter hole (1255d) and the upper end (1254a) of the eccentric section (1254). In the former case, that is, when the gap (G1) is formed to be larger than the gap (G2), the oil discharged through the oil scatter hole (1255d) can be scattered further toward the compression section (130) along the scatter guide section (1273) while maximizing the cross-sectional area of ​​the oil scatter hole (1255d). On the other hand, in the latter case, that is, a part of the oil scattering hole (1255d) is blocked by the oil scattering section (more precisely, the fixed section) (1273), so the cross-sectional area of ​​the oil scattering hole (1255d) is slightly reduced, but the scattering effect may be enhanced as the oil discharged through the oil scattering hole (1255d) collides with the fixed section (1271). In this embodiment, as shown in FIG. 6, an example is illustrated in which the gap (G1) between the upper end (1254a) of the eccentric section (1254) and the upper surface (1273a) of the scattering guide section (1273) is formed to be larger than the gap (G2) between the upper end (1254a) of the eccentric section (1254) and the center (Oh) of the oil scattering hole (1255d).

[0116] For example, the scatter guide section (1273) according to the present embodiment may be formed such that its upper surface (1273a) is located at the same height as the lower end (P2) of the oil scatter hole (1255d), that is, the upper surface (1273a) of the scatter guide section (1273) is located at the same height as the lower end (P2) of the oil scatter hole (1255d). Accordingly, a portion of the oil scattered from the oil passage (1255) may be guided along the upper surface (1273a) of the scatter guide section (1273) toward the cylinder (1314) and reach near the highest point (P1) of the cylinder (1314).

[0117] Additionally, the scatter guide (1273) according to the present embodiment may be formed such that at least a portion of it is located on a virtual line (CL) passing through the center of gravity (Om) of the eccentric mass (1272) and the center (Os) of the eccentric part (1254) of the crankshaft (125). For example, the scatter guide (1273) may be formed so that both sides in the circumferential direction are symmetrical with respect to the virtual line (CL). Accordingly, even if the scatter guide (1273) extends radially from one side in the circumferential direction of the eccentric mass (1272), the center of gravity of the balance weight (127) is located on the aforementioned virtual line (CL), thereby effectively offsetting the eccentric load caused by the eccentric part (1254) of the crankshaft (125).

[0118] In addition, the scatter guide section (1273) according to the present embodiment may be formed within a predetermined scatter guide section (S). For example, the scatter guide section (1273) may be formed within the range of the scatter guide section (S), which is defined as a section of approximately ±45° on both sides in the circumferential direction based on the virtual line (CL) as shown in FIG. 7. Accordingly, by suppressing the scatter guide section (1273) from being formed excessively wide in the circumferential direction, even if the scatter guide section (1273) is formed on the opposite side of the eccentric mass section (1272), the reduction of the eccentric load offsetting effect of the eccentric mass section (1272) caused by the scatter guide section (1273) can be suppressed.

[0119] In this case, the scatter guide section (1273) may be formed only in a part of the scatter guide section (S) described above, or it may be formed over the entire section of the scatter guide section (S). In the former case, while forming the scatter guide section (1273), the reduction of the eccentric load offset effect of the eccentric mass section (1272) according to the scatter guide section (1273) is suppressed, and at the same time, the increase in weight of the balance weight (127) is minimized, thereby suppressing the decrease in motor efficiency. In the latter case, the area of ​​the scatter guide section (1273) is formed as wide as possible so that a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be guided more smoothly between the cylinder (1314) and the piston (132). This embodiment is described with the former case as an example, and the latter is described in another embodiment.

[0120] Additionally, the scatter guide (1273) according to the present embodiment may be formed with a tapered shape in which the two sides in the circumferential direction are parallel or the gap between the two sides narrows in the direction away from the fixed part (1271). Accordingly, while minimizing the area of ​​the scatter guide (1273), the radial length of the scatter guide (1273) is formed as long as possible, so that a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be smoothly guided between the cylinder (1314) and the piston (132).

[0121] In this case, the circumferential length (L1) of the scatter guide (1273) may be formed to be greater than or equal to the radial length (L2). In other words, the circumferential length (L1) of the scatter guide (1273) may be formed to be less than or equal to the length (L2) between the inner surface of the fixed part (1271) and the radial end (hereinafter abbreviated as end) (1273b) of the scatter guide (1273). Accordingly, while minimizing the radial length (L2) of the scatter guide (1273), a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be smoothly guided between the cylinder (1314) and the piston (132). However, in some cases, the circumferential length (L1) of the scatter guide (1273) may be formed to be smaller than the radial length (L2). In this case, the radial length (L2) of the scatter guide (1273) can be formed to be as long as possible to further increase the scatter distance. This will be explained again later in another embodiment.

[0122] Here, the radial length (L2) of the scatter guide (1273) can be formed within a range where the scatter guide (1273) does not collide with the cylinder (1314). For example, as shown in FIG. 7, the scatter guide (1273) can be formed such that the distance (L3) between the center of rotation (Oc) of the crankshaft (125) and the end (1273b) of the scatter guide (1273) is smaller than the shortest distance (L4) between the center of rotation (Oc) of the crankshaft (125) and the end (1314a) of the cylinder (1314). Accordingly, when the balance weight (127) rotates together with the crankshaft (125), the scatter guide (1273) of the balance weight (127) can stably guide oil toward the cylinder (1314) and the piston (132) without colliding with the cylinder (1314).

[0123] In addition, in this case, the circumferential length (L1) of the scatter guide (1273) can be increased or decreased in conjunction with the inner diameter (D1) of the oil scatter hole (1255d). For example, as shown in FIG. 7, the circumferential length (L1) of the scatter guide (1273) can be formed to be greater than or equal to the inner diameter (D1) of the oil scatter hole (1255d). Accordingly, the circumferential length (L1) of the scatter guide (1273) is appropriately set according to the size of the oil scatter hole (1255d), so that the oil scattered from the oil scatter hole (1255d) can be smoothly guided between the cylinder (1314) and the piston (132).

[0124] Meanwhile, the scatter guide section (1273) according to the present embodiment may be formed such that the gap between the two circumferential sides gradually narrows as it moves away from the fixed section (1271). In other words, the outer surface of the scatter guide section (1273) may be formed in an arc shape that extends convexly from the outer surface of the fixed section (1271). Accordingly, the circumferential side of the scatter guide section (1273) forms a curved surface, thereby suppressing performance degradation caused by flow resistance during the rotation of the crankshaft (125). However, in some cases, the two circumferential sides of the scatter guide section (1273) may be formed parallel to each other. In this case, the surface area relative to the radial length (L2) of the scatter guide section (1273) can be expanded to further enhance the lubrication effect. This will be explained again later in another embodiment.

[0125] Furthermore, the scatter guide portion (1273) according to the present embodiment may be formed with the same thickness as the fixed portion (1271). In other words, the thickness (t2) of the scatter guide portion (1273) may be formed with the same thickness as the thickness (t1) of the fixed portion (1271). Accordingly, the scatter guide portion (1273) can be easily formed by extending from the fixed portion (1271) with the same thickness.

[0126] However, in some cases, the thickness (t2) of the scatter guide (1273) may be formed to be thinner than the thickness (t1) of the fixed part (1271). Accordingly, the weight of the scatter guide (1273) is reduced, and the circumferential length (L1) and / or radial length (L2) of the scatter guide (1273) can be increased to increase the amount of fuel supplied to the compression part (130).

[0127] Furthermore, the scatter guide section (1273) according to the present embodiment may be formed at the same height as the fixed section (1271). In other words, the upper surface (1273a) of the scatter guide section (12) may be formed to be flush with the upper surface (1271b) of the fixed section (1271). Accordingly, the scatter guide section (1273) can be easily processed while guiding the oil discharged through the oil scatter hole (1255d) to scatter far toward the cylinder (1314).

[0128] However, in some cases, the upper surface (1273a) of the scatter guide (1273) may be formed to be inclined or curved so that it becomes higher in the axial direction from the inner side to the outer side of the scatter guide (1273). In this case, the scatter guiding effect under conditions where the circumferential length (L1) and / or radial length (L2) of the scatter guide (1273) are the same can be further enhanced. This will be explained again later in another embodiment.

[0129] Meanwhile, although not illustrated in the drawing, the scatter guide section (1273) may be formed such that at least a portion overlaps with the virtual line (CL), while the circumferential sides are formed asymmetrically relative to the virtual line (CL). For example, the scatter guide section (1273) may be formed such that a portion overlaps with the virtual line (CL) but is eccentrically formed in the opposite direction to the rotational direction of the crankshaft (125). Accordingly, a large amount of oil can be smoothly guided toward the cylinder (1314) and piston (132) from the oil scattering hole (1255d) while minimizing the area of ​​the scatter guide section (1273).

[0130] As described above, when the scatter guide (1273) extends radially from the outer surface of the fixed part (1271), the actual distance from the oil scatter hole (1255d) to the compression part (130) can be shortened. Then, a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be guided more effectively between the cylinder (1314) and the piston (132) of the compression part (130) through the scatter guide (1273). Through this, oil is smoothly supplied between the cylinder (1314) and the piston (132) during low-speed operation as well as high-speed operation, thereby suppressing refrigerant leakage in the compression chamber (130a) to increase cooling power, and at the same time, reducing friction loss between the cylinder (1314) and the piston (132), thereby increasing compressor performance. In addition, the oil splash distance can be extended without adding a separate component, allowing oil to be supplied smoothly between the cylinder (1314) and the piston (132).

[0131] This can also be confirmed through FIGS. 8a and 8b. FIGS. 8a and 8b are schematic diagrams showing the simulated scattering distance by driving speed depending on the presence or absence of the scattering guide (1273).

[0132] Referring to FIG. 8a, when there is no scatter guide (1273), under the condition of 15 rps where the crankshaft (125) is operated at a relatively low speed, a large amount of oil among the oil scattered from the crankshaft (125) reaches a height that is approximately 2 / 3 of the peak (P1) of the cylinder (1314), and even under the condition of 30 rps where it is operated at a relatively high speed, the oil scattered from the crankshaft (125) barely reaches the peak (P1) or near the peak (P1) of the cylinder (1314).

[0133] However, referring to FIG. 8b, when the scatter guide (1273) is present, even under the condition of 15 rps, when the crankshaft (125) is operated at a relatively low speed, a large amount of oil among the oil scattered from the crankshaft (125) reaches a height that is approximately 4 / 5 of the peak (P1) of the cylinder (1314), and under the condition of 30 rps, when operated at a relatively high speed, a large amount of oil among the oil scattered from the crankshaft (125) reaches a height that exceeds the peak (P1) of the cylinder (1314). Accordingly, when the scatter guide (1273) as in this embodiment is provided, a large amount of oil among the oil scattered from the crankshaft (125) is scattered further toward the compression section (130), thereby lubricating the space between the cylinder (1314) and the piston (132) more effectively. Through this, the cooling power and / or efficiency of the reciprocating compressor can be improved by smoothly lubricating the space between the cylinder (1314) and the piston (132) to reduce friction loss, while effectively sealing the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132) to suppress refrigerant leakage in the compression chamber (130a).

[0134] This can also be confirmed through Figures 9a and 9b. Figures 9a and 9b are graphs comparing cooling power and energy efficiency by operating speed with and without a scatter guide.

[0135] Referring to FIG. 9a, it can be seen that the cooling power [Q] of the compressor at a relatively low speed is improved by approximately 1.3% when the balance weight (127) is equipped with a scatter guide (1273) (hereinafter, the present embodiment) compared to when there is no scatter guide (1273) (hereinafter, the conventional). In other words, when the crankshaft (125) rotates at a speed of 17 rps, the cooling power in the conventional embodiment was approximately 89.35 W, but the cooling power in the present embodiment is approximately 90.55 W. Accordingly, it can be seen that the cooling power of the compressor when the crankshaft (125) rotates at a relatively low speed of 17 rps is improved by approximately 1.3% in the present embodiment compared to the conventional one.

[0136] On the other hand, it can be seen that the cooling power [Q] of the compressor at a relatively high speed is improved by approximately 0.5% in this embodiment compared to the conventional one. In other words, when the crankshaft (125) rotates at a speed of 30 rps, the cooling power in the conventional one was approximately 154.31 W, but the cooling power in this embodiment is approximately 155.07 W. Accordingly, it can be seen that the cooling power of the compressor when the crankshaft (125) rotates at a relatively high speed of 30 rps is improved by approximately 0.5% in this embodiment compared to the conventional one.

[0137] Additionally, referring to FIG. 9b, it can be seen that the compressor efficiency [EER] at a relatively low speed is improved by approximately 0.8% in this embodiment compared to the conventional one. In other words, when the crankshaft (125) rotates at a speed of 17 rps, the compressor efficiency in the conventional one was approximately 9.22 W, whereas the compressor efficiency in this embodiment is approximately 9.30 W. Accordingly, it can be seen that the compressor efficiency in this embodiment is improved by approximately 0.8% compared to the conventional one when the crankshaft (125) rotates at a relatively low speed of 17 rps.

[0138] On the other hand, it can be seen that the compressor efficiency [EER] at a relatively high speed is improved by approximately 0.6% in this embodiment compared to the conventional one. In other words, when the crankshaft (125) rotates at a speed of 30 rps, the compressor efficiency in the conventional one was approximately 8.95 W, but in this embodiment, the compressor efficiency is approximately 9.012 W. Accordingly, it can be seen that the compressor efficiency in this embodiment is improved by approximately 0.6% compared to the conventional one when the crankshaft (125) rotates at a relatively high speed of 30 rps. Through this, it can be seen that when a balance weight (127) is applied to the eccentric part (1254) of the crankshaft (125), and a scatter guide part (1273) is formed on the balance weight (127) that extends to the opposite side of the eccentric mass part (1272), that is, toward the compression part (130), the cooling power and compressor efficiency of the compressor are improved, and this is further improved, especially in low-speed operation.

[0139] Meanwhile, other embodiments of the balance weight are as follows.

[0140] That is, in the above-described embodiment, the circumferential length of the scatter guide is formed to be greater than or equal to the radial length, but in some cases, the circumferential length of the scatter guide may be formed to be smaller than the radial length.

[0141] FIG. 10 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0142] Referring to FIG. 10, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of the fixed part (1271), the eccentric mass part (1272), and the scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0143] However, in this embodiment, the circumferential length (L1) of the scatter guide (1273) may be formed to be smaller than the radial length (L2). In other words, the scatter guide (1273) may be formed to be longer in the radial direction than in the circumferential direction. In this case, the end (1273b) of the scatter guide (1273) may be extended to a position closer to the cylinder (1314) and the piston (132).

[0144] As described above, if the circumferential length (L1) of the scatter guide (1273) is formed to be smaller than the radial length (L2), the radial length (L2) of the scatter guide (1273) can be extended further toward the cylinder (1314). Then, the end (1273b) of the scatter guide (1273) can be extended closer to the cylinder (1314). Accordingly, even if the circumferential length (L1) of the scatter guide (1273) is reduced compared to the previously described embodiment, a large amount of oil among the oil scattered from the crankshaft (125) during low-speed operation as well as high-speed operation can reach the vicinity of the highest point (P1) of the cylinder (1314). By doing so, the circumferential length (width) (L1) of the scatter guide (1273) is formed to be small, and the space between the cylinder (1314) and the piston (132) is lubricated more smoothly to reduce friction loss, while simultaneously suppressing the leakage of refrigerant from the compression chamber (130a) through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132), thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0145] Meanwhile, another embodiment of the balance weight is as follows.

[0146] That is, in the above-described embodiment, the scatter guide is formed in a circular or arc shape, but in some cases, the outer surface of the scatter guide may be formed in a rectangular shape.

[0147] FIG. 11 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0148] Referring to FIG. 11, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of the fixed part (1271), the eccentric mass part (1272), and the scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0149] However, in this embodiment, the scatter guide (1273) may be formed as a rectangular shape that is long in the radial direction. For example, at least a portion of the gap between the two circumferential sides of the scatter guide (1273) may be formed equally along the radial direction, that is, the two circumferential sides may be formed parallel to each other. Accordingly, the surface area of ​​the upper surface (1273a) of the scatter guide (1273) may be increased under the condition that the circumferential length (L1) and / or radial length (L2) of the scatter guide (1273) are the same.

[0150] In this case, the scatter guide section (1273) may be formed such that the radial length (L2) is longer than the circumferential length (L1), or conversely, the circumferential length (L1) is longer than the radial length (L2). In the former case, the scatter guide section (1273) may be closer to the cylinder (1314) to guide the scattering of oil, and in the latter case, the scatter guide section (S) of the scatter guide section (1273) may be expanded. This embodiment illustrates an example in which the radial length (L2) of the scatter guide section (1273) is formed to be longer than the circumferential length (L1).

[0151] In addition, in this case, the end (1273b) of the scatter guide (1273) connecting both circumferential sides of the scatter guide (1273) may be formed as a straight surface or a curved surface. This embodiment illustrates an example in which the end (1273b) of the scatter guide (1273) is formed as a straight surface.

[0152] As described above, when the scatter guide (1273) is formed as a rectangular shape or a rectangular shape with curved corners, the circumferential length of the scatter guide (1273) may remain the same compared to the previously described embodiments, while the total area may increase. Accordingly, even if the radial length (L2) of the scatter guide (1273) is the same as the previously described embodiments or is reduced compared to the previously described embodiments, a large amount of oil among the oil scattered from the crankshaft (125) during low-speed operation as well as high-speed operation may reach the vicinity of the highest point (P1) of the cylinder (1314). By doing so, the radial length (L2) of the scatter guide (1273) is formed to be small, and the space between the cylinder (1314) and the piston (132) is lubricated more smoothly to reduce friction loss, while simultaneously suppressing the leakage of refrigerant from the compression chamber (130a) through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132), thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0153] Although not illustrated in the drawing, the circumferential length (L1) of the scatter guide (1273) may be formed to increase as it moves further away from the fixed part (1271). In this case, the area of ​​the scatter guide (1273) may be increased more than in the previously described embodiments. Through this, even if the radial length (L2) of the scatter guide (1273) is further reduced, the area at the scatter guide (specifically, the end of the scatter guide) (1273) increases, allowing a large amount of oil among the oil scattered through the oil scatter hole (1255d) to be guided more smoothly between the cylinder (1314) and the piston (132).

[0154] Meanwhile, another embodiment of the balance weight is as follows.

[0155] That is, in the above-described embodiment, the scatter guide portion of the balance weight is formed symmetrically on both sides in the circumferential direction with respect to a virtual line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion, but in some cases, the scatter guide portion may be formed eccentrically with respect to the virtual line.

[0156] FIG. 12 is a plan view showing a balance weight equipped with a scatter guide section of another embodiment.

[0157] Referring to FIG. 12, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of the fixed part (1271), the eccentric mass part (1272), and the scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof will be replaced by the description of the previously described embodiment.

[0158] However, in this embodiment, the scatter guide (1273) may be formed eccentrically along the circumferential direction while extending radially from the outer surface of the fixed part (1271). For example, the scatter guide (1273) may be formed eccentrically so as to be spaced apart by a predetermined distance in the circumferential direction from a virtual line (CL) passing through the center of gravity (Om) of the eccentric mass part (1272) and the center (Os) of the eccentric part (1254). In this case, the scatter guide (1273) may be formed eccentrically in the direction in which centrifugal force acts, that is, in the direction of reverse rotation of the crankshaft (125) corresponding to the downstream side with respect to the virtual line (CL). Accordingly, a large amount of oil can be smoothly guided toward the cylinder (1314) and piston (132) from the oil scattering hole (1255d) while forming the area of ​​the scatter guide (1273) to a minimum.

[0159] As described above, when the scatter guide (1273) is formed eccentrically in the reverse rotation direction of the crankshaft (125) relative to the virtual line (CL), most of the oil scattered from the oil scatter hole (1255d) of the crankshaft (125) is scattered to the downstream side relative to the virtual line (CL) by the centrifugal force generated during the rotation of the crankshaft (125). At this time, as the scatter guide (1273) is located downstream from the virtual line (CL), a large amount of oil among the oil scattered from the oil scatter hole (1255d) can travel further along the scatter guide (1273) toward the compression section (130). Accordingly, a large amount of oil scattered from the crankshaft (125) reaches the vicinity of the highest point (P1) of the cylinder (1314) during low-speed operation as well as high-speed operation, thereby allowing for more effective lubrication between the cylinder (1314) and the piston (132). By doing so, the area of ​​the scatter guide (1273) is formed small, and the space between the cylinder (1314) and the piston (132) is smoothly lubricated to reduce friction loss, while simultaneously suppressing the leakage of refrigerant from the compression chamber (130a) through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132), thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0160] Meanwhile, another embodiment of the balance weight is as follows.

[0161] That is, in the aforementioned embodiments, the scattering guide portion of the balance weight is formed in a part of the guide protrusion forming range, but in some cases, the scattering guide portion may be formed over the entire range of the guide protrusion forming range.

[0162] FIGS. 13 and 14 are plan views showing a balance weight equipped with a scatter guide section of another embodiment.

[0163] Referring to FIGS. 13 and 14, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of these fixed part (1271), eccentric mass part (1272), and scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof will be replaced by the description of the previously described embodiment.

[0164] However, in this embodiment, the scatter guide section (1273) may be formed over the entire scatter guide section (S) described above. For example, both ends of the scatter guide section (1273) may be formed to extend to positions that are ±45 degrees in both circumferential directions relative to a virtual line (CL) passing through the center of gravity (Om) of the eccentric mass section (1272) and the center (Os) of the eccentric section (1254) of the crank shaft (125). In this case as well, the scatter guide section (1273) may be formed symmetrically on both circumferential sides relative to the virtual line (CL) as described above, or may be formed asymmetrically.

[0165] In addition, in this case, as shown in FIG. 13, the gap between the two circumferential sides of the scatter guide (1273) may be formed such that the gap between the two circumferential sides narrows as it moves away from the fixed part (1271), or as shown in FIG. 14, the gap between the two circumferential sides may be formed such that it is the same along the radial direction. In the former case, the scatter guide section (S) is secured as wide as possible while reducing the weight of the scatter guide (1273), whereas in the latter case, the scatter guide section (S) is secured as wide as possible so that the distance of oil scattering by the scatter guide (1273) can be secured far even during low-speed operation.

[0166] As described above, when the scatter guide section (1273) is formed over the entire scatter guide section (S), the circumferential length (L1) of the scatter guide section (1273) increases, thereby increasing the amount of effective oil guided toward the cylinder (1314) by the scatter guide section (1273) from the oil scattering hole (1255d). Then, even if the radial length (L2) of the scatter guide section (1273) is reduced compared to the previously described embodiments, a large amount of oil from the oil scattering from the crankshaft (125) can reach the vicinity of the highest point (P1) of the cylinder (1314). Accordingly, the radial length (L2) of the scatter guide (1273) is formed to be small, while simultaneously lubricating the space between the cylinder (1314) and the piston (132) more smoothly, and effectively sealing the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132). Through this, the space between the cylinder (1314) and the piston (132) is lubricated smoothly to reduce friction loss, and at the same time, the leakage of refrigerant from the compression chamber (130a) through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132) is suppressed, thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0167] Meanwhile, another embodiment of the balance weight is as follows.

[0168] That is, in the aforementioned embodiments, the upper surface of the scatter guide portion of the balance weight is formed flat, but in some cases, the upper surface of the scatter guide portion may be formed inclined or curved.

[0169] FIG. 15 is a cross-sectional view showing a balance weight equipped with a scatter guide section of another embodiment.

[0170] Referring to FIG. 15, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of these fixed part (1271), eccentric mass part (1272), and scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0171] However, in this embodiment, the upper surface (1273a) of the scatter guide (1273) may not be flat; in other words, the upper surface (1273a) of the scatter guide (1273) may be formed with a higher height on the side further away from the fixed part (1271) than on the side adjacent to the fixed part (1271). For example, the upper surface (1273a) of the scatter guide (1273) may be formed in a sloped or curved shape so that it becomes progressively higher from the fixed part (1271) to the end (1273b) of the scatter guide (1273). Even in this case, as previously explained, the scatter guide (1273) may be formed so that both sides in the circumferential direction are symmetrical to each other with respect to the aforementioned virtual line (CL), or may be formed asymmetrically to each other. In addition, in this case, the scatter guide section (1273) may be formed such that the distance between the two circumferential sides, i.e., the circumferential length (L1), becomes narrower as it moves away from the fixed section (1271), or the circumferential length (L1) may be formed uniformly along the radial direction. In addition, in this case, the scatter guide section (1273) may be formed in a part of the scatter guide section (S) described above, or it may be formed over the entire section of the scatter guide section (S). The effects of each of these embodiments may be similar to those described above.

[0172] As described above, when the upper surface (1273a) of the scatter guide (1273) is inclined or curved, the oil scattered from the oil scatter hole (1255d) moves upward along the upper surface (1273a) of the scatter guide (1273) and scatters radially. Then, even during low-speed operation as well as high-speed operation, the oil can be scattered further from the oil scatter hole (1255d) toward the cylinder (1314) and piston (132). Then, even if the circumferential length (L1) and / or radial length (L2) of the scatter guide (1273) is reduced compared to the previously described embodiments, a large amount of oil among the oil scattered from the crankshaft (125) can reach the vicinity of the highest point (P1) of the cylinder (1314). Accordingly, the area of ​​the scatter guide (1273) is formed to be small, while simultaneously lubricating the space between the cylinder (1314) and the piston (132) more smoothly, and effectively sealing the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132). Through this, the space between the cylinder (1314) and the piston (132) is lubricated smoothly to reduce friction loss, and at the same time, the leakage of refrigerant from the compression chamber (130a) through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132) is suppressed, thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0173] Meanwhile, another embodiment of the balance weight is as follows.

[0174] That is, in the aforementioned embodiments, the scatter guide of the balance weight is located at the same height as the bottom of the oil passage outlet, but in some cases, the scatter guide may be located lower than the bottom of the oil passage outlet.

[0175] FIG. 16 is a cross-sectional view showing another embodiment of the assembly position of the balance weight according to the present embodiment.

[0176] Referring to FIG. 16, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of the fixed part (1271), the eccentric mass part (1272), and the scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0177] However, in this embodiment, the fixed part (1271) may be connected at a position lower than the outlet of the oil passage (1255), that is, the scatter guide part (1273) may be connected at a position lower than the bottom (P2) of the oil scatter hole (1255d). Accordingly, the fixed part (1271) of the balance weight (127) may not excessively block the oil scatter hole (1255d) due to machining error and / or assembly error of the balance weight (127), thereby increasing the assemblability and / or reliability of the balance weight (127).

[0178] In this case, the scatter guide (1273) may be provided at a position adjacent to the oil scatter hole (1255d), where the upper surface (1273a) of the scatter guide (1273) is lower than the lower surface (P2) of the oil scatter hole (1255d). For example, the scatter guide (1273) may be coupled at a position where the gap (G3) between the upper surface (1273a) of the scatter guide (1273) and the center (Oh) of the oil scatter hole (1255d) is smaller than or equal to the inner diameter (D1) of the oil scatter hole (1255d). Accordingly, the assembly and / or reliability of the balance weight (127) is improved, while the scatter guide portion (1273) of the balance weight (127) is not too far from the bottom (P2) of the oil scatter hole (1255d), so that oil can be smoothly guided between the cylinder (1314) and the piston (132).

[0179] In addition, in this case, the scatter guide section (1273) may be formed symmetrically on both sides in the circumferential direction with respect to the aforementioned virtual line (CL) as described above, or asymmetrically. In addition, in this case, the scatter guide section (1273) may be formed such that the circumferential length (L1) narrows as it moves away from the fixed section (1271), or the circumferential length (L1) may be formed uniformly along the radial direction. In addition, in this case, the upper surface (1273a) of the scatter guide section (1273) may be formed flat, or it may be formed inclined or curved so that it becomes higher as it approaches the end (1273b) of the scatter guide section (1273). In addition, in this case, the scatter guide section (1273) may be formed in a part of the scatter guide section (S) described above, or it may be formed over the entire section of the scatter guide section (S). The effects of each of these embodiments may be similar to those described above.

[0180] As described above, when the scatter guide (1273) is fixed at a distance lower than the bottom (P2) of the oil scatter hole (1255d), that is, at a distance smaller than or equal to the inner diameter (D1) of the oil scatter hole (1255d), the scatter guide (1273) is not separated too far from the oil scatter hole (1255d). Accordingly, a large amount of oil among the oil scattered from the oil scatter hole (1255d) can be smoothly supplied between the cylinder (1314) and the piston (132) by traveling along the scatter guide (1273). This prevents the fixed part (or scatter guide part) (1271) of the balance weight (127) from blocking the oil scatter hole (1255d) due to processing error and / or assembly error of the balance weight (127), thereby allowing the oil sucked through the oil passage (1255) to be smoothly supplied to the compression part (130) and / or the electric part.

[0181] Meanwhile, another embodiment of the balance weight is as follows.

[0182] That is, in the aforementioned embodiments, an oil splash hole is formed by penetrating the eccentric portion of the crankshaft, but in some cases, an oil passage may be formed by penetrating the upper part of the eccentric portion.

[0183] FIG. 17 is a cross-sectional view showing another embodiment of the assembly position of the balance weight according to the present embodiment.

[0184] Referring to FIG. 17, the basic configuration of the balance weight (127) according to the present embodiment and the resulting effects are similar to those of the previously described embodiment. For example, the balance weight (127) according to the present embodiment may include a fixed part (1271) that is inserted into and fixed to the eccentric part (1254) of the crankshaft (125), an eccentric mass part (1272) that extends radially from one side of the outer surface of the fixed part (1271) to form an eccentric load, and a scattering guide part (1273) that extends radially from the other side of the outer surface of the fixed part (1271) to guide oil scattered from the crankshaft (125) toward the compression part (130). Since the basic configuration of the fixed part (1271), the eccentric mass part (1272), and the scattering guide part (1273) and the resulting effects are almost identical to those of the previously described embodiment, the description thereof is replaced by the description of the previously described embodiment.

[0185] However, in this embodiment, one end forming the outlet of the oil passage may be formed by penetrating through the upper end (1254a) of the eccentric part (1254) of the crankshaft (125). In other words, the oil splash hole (1255d) in the previously described embodiments may be excluded (or even if an oil splash hole is formed), and the outlet end of the oil passage (1255) may be formed by penetrating through the upper end (1254a) of the eccentric part (1254) of the crankshaft (125). In this case, the fixed part (1271) of the balance weight (127) may be inserted into and coupled to the outer circumference of the eccentric part (1254), and may be fixedly coupled near the upper end (1254a) of the eccentric part (1254). In other words, the scatter guide (1273) can be joined at a position where the gap (G1') between the upper surface (1273a) of the scatter guide (1273) and the upper end (1254a) of the eccentric part (1254) is smaller than or equal to the inner diameter (D2) of the third oil passage (1255c) at the upper end of the eccentric part.

[0186] For example, the upper surface (1271b) of the fixed part (1271), that is, the upper surface (1273a) of the scatter guide part (1273), can be joined so as to be aligned with the upper end (1254a) of the eccentric part (1254). In this case, as previously explained, the scatter guide part (1273) may be formed so that both sides in the circumferential direction are symmetrical to each other with respect to the aforementioned virtual line (CL), or may be formed asymmetrically to each other. In addition, in this case, the scatter guide part (1273) may be formed so that the circumferential length (L1) becomes narrower as it moves away from the fixed part (1271), or the circumferential length (L1) may be formed equally along the radial direction. In addition, in this case, the upper surface (1273a) of the scatter guide section (1273) may be formed flat, or it may be formed inclined or curved so as to become higher toward the end (1273b) of the scatter guide section (1273). In addition, in this case, the scatter guide section (1273) may be formed in a part of the scatter guide section (S) described above, or it may be formed over the entire section of the scatter guide section (S). The effects of each of these embodiments may be similar to those described above.

[0187] As described above, when the outlet of the oil passage (1255) penetrates the upper end (1254a) of the eccentric part (1254) of the crankshaft (125), the fixed part (1271) of the balance weight (127) can be coupled so that, for example, the upper surface (1273a) of the scatter guide part (1273) is aligned with the upper end (1254a) of the eccentric part (1254), that is, so that they form the same plane. Then, a portion of the oil scattered from the oil passage (1255) can be guided along the upper surface (1273a) of the scatter guide part (1273) toward the cylinder (1314) and reach the vicinity of the highest point (P1) of the cylinder (1314). Accordingly, the crankshaft (125), including the oil passage (1255), can be easily machined while smoothly lubricating the space between the cylinder (1314) and the piston (132), and effectively sealing the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132). Through this, friction loss is reduced by smoothly lubricating the space between the cylinder (1314) and the piston (132), and at the same time, the refrigerant in the compression chamber (130a) is prevented from leaking through the gap between the inner surface of the cylinder (1314) and the outer surface of the piston (132), thereby improving the cooling power and / or efficiency of the reciprocating compressor.

[0188] Although not illustrated in the drawing, the fixed portion (1271) of the balance weight (127) may be connected at a predetermined distance from the upper portion (1254a) of the eccentric portion (1254) of the crankshaft (125). In this case, the gap (G1) between the upper portion (1254a) of the eccentric portion (1254) and the upper surface (1271b) of the fixed portion (1271) of the balance weight (127) may be formed to be smaller than or equal to the inner diameter (D2) of the oil passage (1255). The effect of this may be similar to that of the embodiment of FIG. 16 described above.

[0189] Meanwhile, in the embodiments described above, the scatter guide portion (1273) is extended from the fixed portion (1271), but in some cases, the scatter guide portion (1273) in the embodiments described above may be excluded and only the fixed portion (1271) may be formed. In other words, even if the scatter guide (1273) is excluded from the fixed part (1271), if the fixed part (1271) is positioned in alignment with the lower end (P2) of the oil scatter hole (1255d) and / or the upper end (1254a) of the eccentric part (1254) that forms the outlet height of the oil passage (1255), or if it is positioned at a lower position than the lower end (P2) of the oil scatter hole (1255d) and / or the upper end (1254a) of the eccentric part (1254) (for example, a position where the gap between the upper surface of the fixed part and the center of the oil scatter hole and / or the upper end of the eccentric part is smaller than the inner diameter of the oil scatter hole and / or the inner diameter of the oil passage), then a large amount of oil among the oil scattered from the oil passage (1255) can be scattered further along the upper surface (1271b) of the fixed part (1271) toward the cylinder (1314). The resulting effects are replaced by the description of the aforementioned embodiments.

Claims

1. A shell in which a predetermined amount of oil is stored; A driving unit provided inside the above shell and providing driving force; A compression unit that compresses the refrigerant as the piston reciprocates inside the cylinder by the driving force of the above-mentioned electric unit; A crankshaft having an eccentric portion eccentric with respect to a rotational center and an oil passage so that oil stored in the shell is sucked toward the eccentric portion; and It includes a balance weight coupled to the eccentric portion of the crankshaft and rotating together with the crankshaft, The above balance weight is, A fixed part coupled to the eccentric portion of the crankshaft above; An eccentric mass portion extending radially eccentrically from the above fixed portion; and A reciprocating compressor comprising a scatter guide extending from the fixed portion in a direction opposite to the eccentric mass portion and guiding oil scattered from the oil passage toward the compression portion.

2. In Paragraph 1, The above scatter guide is, A reciprocating compressor formed such that at least a portion is located on a virtual line passing through the center of gravity of the eccentric mass portion and the center of the eccentric portion of the crankshaft.

3. In Paragraph 2, The above scatter guide is, A reciprocating compressor in which both sides in the circumferential direction are formed symmetrically with respect to the above virtual line.

4. In Paragraph 2, The above scatter guide is, A reciprocating compressor formed asymmetrically so as to be eccentric to the opposite side of the rotational direction of the crankshaft relative to the above virtual line.

5. In Paragraph 1, The above scatter guide is, A reciprocating compressor formed eccentrically on one side in the circumferential direction with respect to a virtual line passing through the center of gravity of the eccentric mass part and the center of the eccentric part of the crankshaft.

6. In Paragraph 5, The above scatter guide is, A reciprocating compressor formed on the opposite side to the rotational direction of the crankshaft.

7. In Paragraph 1, The above scatter guide is, A reciprocating compressor in which the circumferential length is greater than or equal to the radial length.

8. In Paragraph 1, The above scatter guide is, A reciprocating compressor in which the circumferential length is formed to be less than or equal to the radial length.

9. In Paragraph 1, The above scatter guide is, A reciprocating compressor formed such that the gap between the two circumferential sides narrows as it moves away from the above-mentioned fixed part.

10. In Paragraph 1, The above scatter guide is, A reciprocating compressor in which at least a portion of the gap between the two circumferential sides is formed equally along the radial direction.

11. In Paragraph 1, The distance between the rotational center of the crankshaft and the end of the scatter guide is, A reciprocating compressor formed to be smaller than the shortest distance between the center of rotation of the crankshaft and the end of the cylinder.

12. In Paragraph 1, An oil splash hole is formed in the crankshaft above, extending from the oil passage and penetrating to the outer surface of the eccentric part, and The circumferential length of the above scatter guide is, A reciprocating compressor formed to be larger than or equal to the inner diameter of the oil splash hole.

13. In Paragraph 1, An oil splash hole is formed in the crankshaft above, extending from the oil passage and penetrating to the outer surface of the eccentric part, and The gap between the upper end of the eccentric part and the upper surface of the scattering guide part is, A reciprocating compressor formed to be greater than or equal to the gap between the upper end of the eccentric part and the center of the oil scattering hole.

14. In Paragraph 13, The above scatter guide is, A reciprocating compressor in which the upper surface of the scatter guide is provided at the same height as the lower end of the oil scatter hole.

15. In Paragraph 13, The above scatter guide is provided such that the upper surface of the scatter guide is positioned lower than the lower end of the oil scatter hole, and The gap between the bottom of the oil scattering hole and the upper surface of the scattering guide is, A reciprocating compressor with an inner diameter smaller than or equal to the inner diameter of the oil splash hole mentioned above.

16. In Paragraph 1, The above oil passage is formed by penetrating through the upper end of the above eccentric part, and The gap between the upper end of the eccentric part and the upper surface of the scattering guide part is, A reciprocating compressor that is smaller than or equal to the inner diameter of the oil passage at the top of the eccentric part.

17. In Paragraph 1, The above scatter guide is, A reciprocating compressor formed with the same thickness as the above-mentioned fixed part.

18. In Paragraph 1, The above scatter guide is, A reciprocating compressor formed thinner than the fixed part above.

19. In Paragraph 1, The above scatter guide is, A reciprocating compressor in which the upper surface is formed in the same plane as the upper surface of the fixed part.

20. In Paragraph 1, The above scatter guide is, A reciprocating compressor in which the upper surface is formed to be inclined or curved so as to become axially higher from the inner side to the outer side of the scatter guide.

21. In any one of paragraphs 1 through 20, The above scatter guide is, A reciprocating compressor formed within a range of ±45 degrees on both sides in the circumferential direction, based on a virtual line passing through the center of gravity of the eccentric mass and the center of the eccentric part of the crankshaft.

22. In Paragraph 21, The above scatter guide is, A reciprocating compressor formed in a portion of the above range.

23. In Paragraph 21, The above scatter guide is, A reciprocating compressor formed over the entire range of the above-mentioned range.

24. A shell in which a predetermined amount of oil is stored; A driving unit provided inside the above shell and providing driving force; A compression unit that compresses the refrigerant as the piston reciprocates inside the cylinder by the driving force of the above-mentioned electric unit; A crankshaft having an eccentric portion eccentric with respect to the center of rotation, and an oil passage provided so that oil stored in the shell is sucked toward the eccentric portion; and It includes a balance weight coupled to the eccentric portion of the crankshaft and rotating together with the crankshaft, An oil splash hole is formed on the outer surface of the eccentric portion through which one end of the oil passage passes, and the balance weight is provided with a fixing portion to wrap around and connect the eccentric portion of the crankshaft. The above fixed part is, A reciprocating compressor coupled at a position where the gap between the upper surface of the fixed part and the center of the oil splash hole is smaller than or equal to the inner diameter of the oil splash hole.

25. In Paragraph 24, The above fixed part is, A reciprocating compressor in which the upper surface of the fixed part is connected at the same height as the lower end of the oil splash hole.

26. In Paragraph 24, The upper surface of the above-mentioned fixed part is, A reciprocating compressor formed to form a coplanar plane along the radial direction.

27. In Paragraph 24, The upper surface of the above-mentioned fixed part is, A reciprocating compressor formed such that the axial height increases from the inner surface to the outer surface of the fixed part.

28. In any one of paragraphs 24 through 27, The above balance weight is, A reciprocating compressor further comprising a scatter guide extending radially from the outer surface of the fixed part and guiding oil scattered from the oil passage toward the compression part.

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