Turbo compressor

Abstract

The present invention provides a turbo compressor comprising: a motor housing; a drive motor; a rotating shaft; first and second impellers respectively coupled to both sides of the rotating shaft to compress a refrigerant being drawn in; and first and second impeller housings for rotatably accommodating the first and second impellers, respectively. A first flow path, which allows the refrigerant compressed by the first impeller to flow, is provided on one side of the first impeller housing, a second flow path, which communicates with the first flow path and supplies the compressed refrigerant to the second impeller housing, is provided in the motor housing, and a third flow path, which communicates with the second flow path and can supply the compressed refrigerant to a suction port of the second impeller, is provided on one side of the second impeller housing.

Description

turbo compressor

[0001] The present invention relates to a turbo compressor, and more particularly, to a turbo compressor that enables compact packaging while reducing the number of parts and without increasing the loss of the conventional turbo compressor compared to the conventional turbo compressor.

[0002] Typically, compressors are used in vapor compression refrigeration cycles (hereinafter referred to as "refrigeration cycles"), such as refrigerators and air conditioners. Depending on the method of compressing the refrigerant, compressors can be categorized into reciprocating, rotary, and scroll types.

[0003] A reciprocating compressor is a compressor that compresses gas through the reciprocating motion of a piston inside a cylinder, and among these, a scroll compressor is a compressor in which a rotating scroll is engaged with a fixed scroll fixed in the internal space of a sealed container and rotates, thereby forming a compression chamber between the fixed wrap of the fixed scroll and the rotating wrap of the rotating scroll.

[0004] A turbocompressor is a type of centrifugal compressor. It compresses gas using centrifugal force by rotating a wheel with curved blades within a casing. Turbocompressors offer advantages over reciprocating and screw compressors, including larger capacity, lower noise, and lower maintenance. Furthermore, they can produce clean, oil-free compressed gas.

[0005] Turbocompressors are similar to turbo blowers, but have higher discharge pressure and lower flow rates. These turbocompressors increase the pressure of a continuously flowing fluid. They can be classified as axial-flow (if the fluid flows axially) or centrifugal (if the fluid flows radially).

[0006] A centrifugal turbocompressor consists of an impeller to compress gas and a diffuser to decelerate the accelerated gas flow and convert it into pressure. When a motor rotates the impeller at high speed, external gas is sucked along the impeller's axial direction and discharged in the centrifugal direction of the impeller. The fluid discharged in the centrifugal direction of the impeller travels along the flow path formed inside the turbocompressor and is compressed.

[0007] Meanwhile, conventional two-stage ultra-compact turbocompressors utilize a separate, externally protruding conduit to connect the compressed refrigerant, which passes through the first-stage impeller and diffuser, to the second-stage impeller. The connecting conduit, which is connected by a volute and bolts that serve as the first-stage discharge and second-stage suction, uses an O-ring to prevent leakage, and the groove for installing this O-ring requires precise machining. In addition, due to the characteristics of the radially located first-stage discharge and axially located second-stage suction, two or more bends are required, and when using standard products, the size and weight of the product may increase due to the connecting conduit.

[0008] The fluid compressed through the impeller and diffuser is discharged through the connecting passage connecting the first and second stages and the second-stage discharge port through the passage inside the volute. Here, the passage inside the volute has the shape of an expansion tube to connect to the inlet of the second-stage impeller. As the distance of the expansion tube shortens and the expansion angle of the expansion tube increases, the loss inside the passage increases.

[0009] To explain in more detail, the protruding 1st and 2nd stage connecting passages of a conventional ultra-small turbo are composed of one U-shaped bent pipe and one straight pipe, and 12 bolts and 3 O-rings or gaskets to prevent leakage are required to connect them.

[0010] In particular, when using an O-ring, additional precision machining is required to create the O-ring groove. Furthermore, when using a gasket, additional mold costs are incurred for gasket manufacturing. Furthermore, when using standard pipe to reduce material costs, the single- and two-stage connection paths can increase the product's packaging size and weight.

[0011] The internal flow path connecting the volute to the connecting section takes the form of an expansion tube, expanding from a small discharge port to the size of a two-stage suction port. Increasing the angle of the expansion tube to reduce the flow path length leads to increased flow separation and internal flow losses.

[0012] The present invention has been devised to solve the above problems, and one object of the present invention is to provide a turbocompressor that enables compact packaging while reducing the number of parts and not increasing the loss of the conventional turbocompressor compared to the conventional turbocompressor.

[0013] Another object of the present invention is to provide a turbocompressor having a reduced overall size, and in particular, a reduced packaging area, compared to conventional turbocompressors.

[0014] Another object of the present invention is to provide a turbocompressor having a structure of a volute and a housing that can eliminate the use of a separate pipe used in the past.

[0015] In order to solve the above problem, the turbocompressor of the present invention includes a motor housing having a motor room; a drive motor provided in the motor room and generating rotational force; a rotational shaft for transmitting the rotational force of the drive motor; first and second impellers respectively coupled to both sides of the rotational shaft for compressing sucked refrigerant; and first and second impeller housings respectively rotatably accommodating the first and second impellers, wherein a first flow path is provided on one side of the first impeller housing to allow the refrigerant compressed in the first impeller to flow, a second flow path is provided on the motor housing to be connected to the first flow path and to provide the compressed refrigerant to the second impeller housing, and a third flow path is provided on one side of the second impeller housing to be connected to the second flow path and to provide the compressed refrigerant to an inlet of the second impeller.

[0016] This allows the first to third flow paths to be integrated within the housing, reducing the overall size compared to existing structures utilizing separate piping. This reduces the packaging area compared to conventional turbocompressors. Furthermore, the number of gaskets previously used to prevent leakage can be reduced from four to two, reducing the overall number of leakage-related components by one-third from seven to two, thereby reducing manufacturing and maintenance costs.

[0017] The first impeller housing is provided with a first flow path receiving projection that protrudes from one surface of the exterior and has the first flow path provided therein.

[0018] The first directional accommodating portion may include a first portion extending in a direction intersecting one surface of the exterior of the first impeller housing; and a second portion extending from an end of the first portion but formed into a curved surface.

[0019] Due to this, the pressure drop in the first flow path of the first flow path receiving portion can be minimized.

[0020] Preferably, the first angle formed by the first part and the extension line extending from the outer surface of the first impeller housing may be 5 degrees or more and 15 degrees or less.

[0021] Due to this, the refrigerant discharged from the first impeller (151) experiences a pressure loss from 7.8 kgf / cm2 to approximately 7.76 kgf / cm2 at a flow path length of 200 mm, resulting in a lower pressure loss than in a flow path to which a separate pipe is applied.

[0022] The first impeller housing may include a first flow wall portion provided on the inside of the first impeller housing and formed parallel to the first portion; and a second flow wall portion connected to the first flow wall portion so as to intersect with the first flow wall portion and spaced apart from the second portion.

[0023] The first flow path may be formed so that the cross-sectional area gradually increases between the first portion and the first flow path wall.

[0024] The first flow wall portion may include a first surface provided adjacent to the first impeller side, and a second surface formed differently from the first surface but provided on the first flow side.

[0025] The first surface and the second surface are formed to form a second angle determined in advance between each other, and the first angle formed by the extension line extending from the first portion to the outer surface of the first impeller housing may be greater than the second angle.

[0026] The above motor housing may be provided with a second flow path receiving projection formed protruding from the outer periphery and having the second flow path provided therein.

[0027] The second flow path is provided inside the second flow path receiving portion, enabling packaging of 179.3 mm wide x 190.6 mm high, which reduces the packaging area by 11.3% compared to the conventional turbo compressor. In addition, the number of gaskets previously used to prevent leakage can be reduced from 4 to 2, and the number of leakage-related parts can be reduced by 1 / 3 from 7 to 2, which reduces manufacturing and maintenance costs.

[0028] The second Euro-shaped vortex and the motor housing can be formed to be in contact from one end to the other without providing a space between them.

[0029] The ends of the first flow passage receiving portion and the third flow passage receiving portion are arranged to be parallel to each other, and the ends of the first flow passage receiving portion and the third flow passage receiving portion are each provided with a first flange portion, and the ends of the second flow passage receiving portion may be provided with a second flange portion so as to be sealingly connected to the first flange portion.

[0030] Due to this, the assembly between the first to third flow passages can be improved, and a flow path can be provided through which the refrigerant discharged from the first impeller can flow to the second impeller side without refrigerant leakage occurring between the first to third flow passages.

[0031] The above second euro-accommodating protrusion may be provided to extend along the axial direction in which the rotation axis extends.

[0032] As the second flow passage is extended axially, the pressure drop in the second flow passage can be minimized.

[0033] The second impeller housing may be provided with a third flow path receiving projection formed protruding from one surface of the exterior and having the third flow path provided therein.

[0034] The first flow path may be provided inside the first impeller housing, the second flow path may be provided inside the motor housing, and the third flow path may be provided inside the second impeller housing.

[0035] The above third euro can be formed into a shape that is folded at least twice.

[0036] The third flow path receiving portion may include a first suction projection portion connected to the second flow path receiving portion and formed parallel to the second flow path receiving portion; a second suction projection portion provided to be connected to the suction port of the second impeller; and a third suction projection portion provided to be connected between the first suction projection portion and the second suction projection portion.

[0037] Due to this, the overall size can be reduced compared to a structure using existing separate piping, so that the packaging area can be reduced compared to a conventional turbo compressor.

[0038] The turbo compressor of the present invention can reduce the overall size compared to a structure using a conventional separate pipe, so that the packaging area can be reduced compared to a conventional turbo compressor.

[0039] In addition, the turbo compressor of the present invention changes the method of fixing the first and second stage shells by integrating the connecting passages of the first compression section and the second compression section into the housing and the volute, and reduces the number of parts used, such as gaskets or O-rings, compared to existing ones, by using a structure in which the volute surrounds the first and second stage shells.

[0040] In addition, the turbo compressor of the present invention can reduce the number of gaskets used to prevent leakage from four to two, and the number of parts related to leakage can be reduced by one-third from seven to two, thereby reducing manufacturing and maintenance costs.

[0041] When integrating the 1-2 stage connecting passages using these separate pipes into the volute and housing, a packaging size of 179.3 mm wide x 190.6 mm high becomes possible, reducing the packaging area by 11.3% compared to the conventional turbocompressor. When integrating the 1-2 stage connecting passages into the housing and volute, the method of fixing the 1-2 stage shells was changed, and their structure was changed to a volute that wraps them. This allowed the number of gaskets previously used to prevent leakage to be reduced from four to two, and the overall number of leakage-related parts was reduced by one-third from seven to two, reducing manufacturing and maintenance costs.

[0042] The present invention can reduce pressure loss due to flow separation while integrating the pipe into the interior of the volute and housing.

[0043] The present invention can improve the assembly between the first to third flow passage accommodating protrusions by the first and second flange portions. In addition, it can provide a flow path through which the refrigerant discharged from the first impeller can flow toward the second impeller without causing refrigerant leakage between the first to third flow passage accommodating protrusions.

[0044] Figure 1 is a schematic diagram showing a refrigeration cycle device to which a turbo compressor according to the present invention is applied.

[0045] Figure 2 is a perspective view of the turbo compressor of the present invention viewed from one side.

[0046] Figure 3 is a perspective view of the turbo compressor of the present invention viewed from another side.

[0047] Figure 4 is an exploded perspective view showing the turbo compressor of the present invention.

[0048] Fig. 5 is a cross-sectional view showing a turbo compressor of the present invention (part AA' of Fig. 2).

[0049] Fig. 6 is a cross-sectional view showing the first flow path in the first impeller housing (part BB' of Fig. 2).

[0050] Fig. 7 is a cross-sectional view showing the angle of the expansion tube adjusted in the first impeller housing of Fig. 6 (BB' part of Fig. 2).

[0051] Figure 8 is a conceptual diagram illustrating the analysis results of turbulence concentration when an existing euro, an integral euro, and an integral euro with an improved angle of the expanded pipe are applied.

[0052] Figure 9 is a graph showing the pressure loss in the connecting passages of the first and second stages according to the Euro shape.

[0053] Hereinafter, a turbo compressor (10) according to the present invention will be described in detail with reference to an embodiment shown in the attached drawing. In this embodiment, a turbo compressor (10) of a double-ended and multi-stage type is described as an example, in which a first impeller (151) and a second impeller (161) are installed at both ends of a rotating shaft, and an outlet of a first compression unit (150) including the first impeller (151) is connected to an inlet of a second compression unit (160) including the second impeller (161).

[0054] In addition, the turbo compressor (10) according to the present embodiment can be applied to a chiller system that supplies cold water to a demand source or a refrigeration cycle system that uses a refrigerant.

[0055] In addition, in the turbo compressor (10) according to the present embodiment, the longitudinal direction of the rotation shaft is defined as the axial direction, and the thickness direction of the rotation shaft is defined as the radial direction, and the suction side of each impeller (or compression section) on the axial line is defined as the front, and the discharge side of each impeller is defined as the rear side, and the front side is defined as the first side, and the rear side is defined as the second side, respectively, and described.

[0056] In this specification, identical or similar reference numbers are assigned to identical or similar components even in different embodiments, and redundant descriptions thereof are omitted.

[0057] Additionally, even if the embodiments are different, a structure applied to one embodiment can be applied to another embodiment as long as there is no structural or functional contradiction.

[0058] Singular expressions include plural expressions unless the context clearly indicates otherwise.

[0059] In describing the embodiments disclosed in this specification, if it is determined that a detailed description of a related known technology may obscure the gist of the embodiments disclosed in this specification, the detailed description is omitted.

[0060] The attached drawings are only intended to facilitate understanding of the embodiments disclosed in this specification, and the technical ideas disclosed in this specification are not limited by the attached drawings, and should be understood to include all modifications, equivalents, or substitutes included in the spirit and technical scope of the present invention.

[0061] Figure 1 is a schematic diagram showing a refrigeration cycle including a turbo compressor (10) according to the present embodiment.

[0062] Referring to Fig. 1, a refrigeration cycle device to which a turbo compressor (10) according to the present embodiment is applied is configured such that a compressor (10), a condenser (20), an expander (30), and an evaporator (40) form a closed loop by a refrigerant circulation pipe (1a). That is, a condenser (20), an expander (30), and an evaporator (40) are sequentially connected to the discharge side of the compressor (10), and an outlet of the evaporator (40) is sequentially connected to the suction side of the compressor (10). Accordingly, the refrigerant compressed in the compressor (10) is discharged toward the condenser (20), and the refrigerant is sequentially passed through the condenser (20), the expander (30), and the evaporator (40) and is then sucked back into the compressor (10), repeating a series of processes.

[0063] As described later, the present invention does not have a refrigerant connection pipe connecting the discharge port of the first impeller (151) and the second suction port (1131) of the second impeller housing (113), and as shown in FIG. 1, a flow path communicating between the first compression unit (150) and the second compression unit (160) is provided inside the turbo compressor (10) housing (110).

[0064] Due to this, the turbo compressor (10) of the present invention can reduce the overall size compared to a structure using a conventional separate pipe, so that the packaging area can be reduced compared to a conventional turbo compressor (10). In addition, the number of parts used can be reduced compared to a conventional structure.

[0065] Fig. 2 is a perspective view of the turbo compressor (10) of the present invention as viewed from one side, and Fig. 3 is a perspective view of the turbo compressor (10) of the present invention as viewed from the other side. In addition, Fig. 4 is an exploded perspective view showing the turbo compressor (10) of the present invention, and Fig. 5 is a cross-sectional view showing the turbo compressor (10) of the present invention.

[0066] Hereinafter, the turbo compressor (10) of the present invention will be described with reference to FIGS. 2 to 5.

[0067] A turbo compressor (10) according to the present embodiment includes a motor housing (110) having a motor room, a drive motor provided in the motor room of the motor housing (110) to generate rotational force, a rotational shaft for transmitting the rotational force of the drive motor, first and second impellers (161) respectively coupled to both sides of the rotational shaft, and first and second impeller housings (112, 113) that respectively accommodate the first and second impellers (161) so as to be able to rotate.

[0068] On one side of the first impeller housing (110), a first flow path (1125d) is provided to allow the discharged refrigerant discharged from the first impeller (151) to flow.

[0069] The motor housing (110) is provided with a second passage (1115d) that is connected to the first passage (1125d) and provides discharged refrigerant to the second impeller housing (113).

[0070] On one side of the second impeller housing (113), a third flow path (1136a) is provided that is connected to the second flow path (1115d) and enables the discharged refrigerant to be supplied to the suction port of the second impeller (161).

[0071] In a conventional two-stage ultra-small turbo compressor (10), a passage formed by a separate pipe protruding externally was utilized to connect the compressed refrigerant passing through the first-stage impeller and diffuser to the second-stage impeller. The connecting passage, which is connected by a volute and bolts that serve as the first-stage discharge portion and the second-stage suction portion, uses an O-ring to prevent leakage, and requires precise processing of a groove for installing the O-ring. In addition, due to the characteristics of the positions of the first-stage discharge portion and the second-stage suction portion, which are located radially and axially, two or more bend pipes are required, and when a standard product is used, the size and weight of the product may increase due to the connecting passage.

[0072] For example, in the present invention, the first flow path (1125d) may be provided inside the first impeller housing (110), the second flow path (1115d) may be provided inside the motor housing (110), and the third flow path (1136a) may be provided inside the second impeller housing (113).

[0073] That is, in the present invention, after the compressed refrigerant is discharged from the first impeller (151), the refrigerant flow path provided to the second impeller (161) may be provided not on the outside of the housing (110) forming the turbo compressor (10) of the present invention, but on the inside of the housing (110).

[0074] The turbo compressor (10) of the present invention does not use a separate pipe, compared to a structure using a conventional separate pipe and a flow path provided on the outside of the housing (110), and in particular, the flow path is provided on the inside of the housing (110).

[0075] Accordingly, the overall size of the turbo compressor (10) can be reduced, so that the packaging area can be reduced compared to the existing turbo compressor (10).

[0076] For example, packaging with a width of 179.3 mm and a height of 190.6 mm became possible, and it was confirmed that the packaging area was reduced by 11.3% compared to the conventional turbo compressor (10).

[0077] In addition, the turbo compressor (10) of the present invention integrates the connecting passages of the first compression unit (150) and the second compression unit (160) into the first and second impeller housings (112, 113) and the motor housing (110), thereby changing the fixing method of the first and second stage shells and reducing the number of parts used, such as gaskets or O-rings, compared to the existing ones, by using a structure in which a volute surrounds them.

[0078] The housing (110) according to the present embodiment forms the exterior of the turbo compressor (10) and may include a motor housing (111), a first impeller housing (112), and a second impeller housing (113).

[0079] In the present invention, as described above, a first flow path (1125d) is provided on one side of the first impeller housing (110). A third flow path (1136a) is provided on one side of the second impeller housing (113). A third flow path (1136a) communicating between the first and second flow paths (1125d, 1115d) is provided in the motor housing (110).

[0080] Referring to FIG. 5, the first impeller housing (112) is provided with a first flow path (1125d). For example, the first impeller housing (110) may include a first flow path receiving projection (1125). The first flow path (1125d) may be provided on the inside of the first flow path receiving projection (1125). The first flow path receiving projection (1125) may be understood as having a configuration that protrudes toward the outside of the first impeller housing (110) to receive the first flow path (1125d). The detailed configuration of the first flow path receiving projection (1125) will be described later, and the first impeller housing (110) will be described first.

[0081] Referring to FIG. 5, the first impeller housing (112) may further include a first suction port (1121), a first impeller receiving portion (1122), a first diffuser (1123), and a first volute (1124).

[0082] The first suction port (1121) may be formed in a direction penetrating both axial side surfaces from the center of the first impeller housing (112). For example, the first suction port (1121) may be opened at the front surface (first side) of the first impeller housing (112) and extend in the axial direction. The first suction port (1121) may be formed in a truncated cone shape in which the inlet end to which the refrigerant suction pipe (115) is connected is wide and the outlet end to which the first impeller receiving portion (1122) is connected is narrow. Accordingly, the flow rate and velocity of the refrigerant sucked through the first suction port (1121) can be increased.

[0083] The first impeller receiving portion (1122) extends from the outlet end of the first suction port (1121) toward the outer surface of the first impeller (151), and the first impeller (151) can be rotatably inserted into the first impeller receiving portion (1122). Accordingly, the first impeller receiving portion (1122) can be defined as a first fixed-side shroud, and the inner surface of the first impeller receiving portion (1122) can be formed to be curved along the shape of the outer surface of the first impeller (151).

[0084] The first diffuser (1123) may extend from the downstream end of the first impeller receiving portion (1122). For example, the first diffuser (1123) may be formed as a space between the first side of the first bearing shell (143) facing the first side (not shown) of the thrust runner (1324) to be described later and the second side (not shown) of the first impeller housing (112) facing it.

[0085] The first volute (1124) may be formed by being connected to the downstream side of the first diffuser (1123). For example, the first volute (1124) may be formed by being recessed in the axial rear surface of the first impeller housing (112). The first volute (1124) may be formed in a ring shape to surround the outer circumference of the first diffuser (1123), and may be formed such that the cross-sectional area gradually increases toward the first flow path (1125d) to be described later.

[0086] The first flow path (1125d) may be formed by penetrating the outer side of the first impeller housing (112) from the center of the circumference of the first volute (1124). Accordingly, the inlet end of the first flow path (1125d) may be connected to the first volute (1124), while the outlet end of the first flow path (1125d) may be connected to the third flow path (1136a) of the second impeller housing (113) via the second flow path (1115d) of the motor housing (110) to be described later.

[0087] The first flow path (1125d) may be understood as a discharge flow path of the first compression unit (150). The first flow path (1125d) may be understood as a flow path through which the refrigerant compressed in the first compression unit (150) flows and is provided to the second flow path (1115d). The first flow path (1125d) may have a portion in which the cross-sectional area gradually increases along the portion where the first portion (1125a) extends in FIGS. 6 and 7.

[0088] The motor housing (111) may be formed in a cylindrical shape with both axial ends open. However, the both ends of the motor housing (111) may be formed with a first flange fastening portion (1111) and a second flange fastening portion (1112) extending radially to be fastened to the first impeller housing (112) and the second impeller housing (113) described later.

[0089] A motor chamber (1114) may be formed inside the motor housing (111). A stator (121), which will be described later, may be press-fitted into the center of the motor chamber (1114). Accordingly, the motor chamber (1114) may be divided into a first space (first chamber) (1114a) toward the first compression unit (150) and a second space (second chamber) (1114b) toward the second compression unit (160) based on the stator (121), which will be described later.

[0090] A bearing support portion (1115), which forms part of a first bearing portion (141) to be described later, may be formed in the middle of the first space (1114a). The bearing support portion (1115) may extend radially toward the rotation axis (130) from the inner surface of the motor housing (111) forming the first space (1114a). However, the bearing support portion (1115) may also be press-fitted into the inner surface of the motor housing (111) or may be fastened using a fastening member (not shown) such as a bolt. An example in which the bearing support portion (1115) according to the present embodiment extends as a single body from the inner surface of the motor housing (111) is illustrated.

[0091] A first radial bearing (145) may be installed between the first impeller shaft portion (132) and the first bearing shell (143). The first radial bearing (145) reduces radial stress between the first impeller shaft portion (132) and the first bearing shell (143), thereby ensuring bearing force. The first radial bearing (145) may be a journal bearing.

[0092] As described above, the second space (1114b) may be substantially connected to the first space (1114a). However, although not illustrated in the drawing, a separate refrigerant connection pipe (not illustrated) may be connected to the motor housing (111) forming the second space (1114b). Accordingly, a portion of the liquid refrigerant that has passed through the condenser (not illustrated) may flow into the second space (1114b), and this liquid refrigerant may flow into the second radial bearing (148) connected to the second space (1114b). Through this, the liquid refrigerant, which is the working fluid, may support the second radial bearing (148) to secure bearing force for the end of the second compression section (160) of the rotary shaft (130) and, at the same time, cool the second radial bearing (148) and the rotary shaft (130) facing it.

[0093] The motor housing (110) is provided with a second flow path (1115d). The second flow path (1115d) is connected to the first flow path (1125d) and supplies the refrigerant discharged from the first compression unit (150) to the second impeller housing (113). For this purpose, the second flow path (1115d) may be connected between the first and third flow paths (1125d, 1136a).

[0094] For example, the motor housing (110) may be provided with a second flow path receiving protrusion (1113) that can accommodate a second flow path (1115d). The second flow path receiving protrusion (1113) will be described later.

[0095] Referring to FIGS. 2 to 5, the second impeller housing (113) can be formed almost symmetrically with the first impeller housing (112) with the electric motor (120) as the center. However, there is some difference in the formation positions of the first flow path receiving portion (1125) and the second flow path receiving portion (1113).

[0096] The second impeller housing (113) is provided with a third flow path (1136a). The inlet side of the third flow path (1136a) is connected to the second flow path (1115d) of the motor housing (110), and the outlet side is connected to the second suction port (1131), thereby enabling the refrigerant discharged from the first compression unit (150) to be supplied to the second impeller (161) through the second suction port (1131).

[0097] For example, the second impeller housing (113) may include a third flow path receiving projection (1136). The third flow path (1136a) may be provided on the inside of the third flow path receiving projection (1136). The third flow path receiving projection (1136) may be understood as having a configuration that protrudes toward the outside of the second impeller housing (113) to receive the third flow path (1136a). The detailed configuration of the third flow path receiving projection (1136) will be described later, and the second impeller housing (113) will be described first.

[0098] The second impeller housing (113) according to the present embodiment may further include a second suction port (1131), a second impeller receiving portion (1132), a second diffuser (1133), a second volute (1134), and a second discharge port (1135). The second suction port (1131) may be formed approximately identically to the first suction port (1121), the second impeller receiving portion (1132) may be formed approximately identically to the first impeller receiving portion (which may be defined as a second fixed-side shroud) (1122), the second diffuser (1133) may be formed approximately identically to the first diffuser (1123), and the second volute (1134) may be formed approximately identically to the first volute (1124).

[0099] The second impeller housing (113) can be formed with a configuration almost similar to that of the first impeller housing (112).

[0100] However, the second impeller housing (113) has a structural difference in that the first flow path (1125d) is formed in the first impeller housing (112) with respect to the structure in which the third flow path (1136a) is formed. The difference between the third flow path (1136a) of the second impeller housing (113) and the first flow path (1125d) of the first impeller housing (112) will be described later.

[0101] For the second impeller housing (113) that is not described, the description for the first impeller housing (112) is replaced.

[0102] The second discharge port (1135) may be formed by penetrating the outer surface of the second impeller housing (113) at the center of the circumference of the second volute (1134). Accordingly, the inlet end of the second discharge port (1135) may be connected to the second volute (1134), while the outlet end may be connected to the condenser (20) via the refrigerant circulation pipe (1a).

[0103] Referring to FIGS. 4 and 5, the electric motor (120) according to the present embodiment may include a stator (121) and a rotor (122).

[0104] The stator (121) may include a stator core (1211) and a stator coil (1212). The stator core (1211) is press-fitted and fixed to the motor housing (111), and the stator coil (1212) may be wound around the stator core (1211). Accordingly, a circumferential gap is generated between the two stator coils (1212), and this circumferential gap becomes a refrigerant passage that connects the first space (1114a) and the second space (1114b) of the motor housing (111) to each other.

[0105] The rotor (122) can be rotatably arranged inside the stator (121) and spaced apart from the inner surface of the stator (121). The rotor (122) includes a rotor core (1221) and a permanent magnet (1222), but the rotor core (1221) can be coupled to the rotation shaft (130) or omitted. When the rotor core (1221) is omitted, the permanent magnet (1222) can be attached to the outer surface of the rotation shaft (130) or mounted inside the rotation shaft (130). This embodiment illustrates an example in which the permanent magnet (1222) is inserted into the interior of the rotation shaft (130) so that a portion of the rotation shaft (130) forms the rotor core (1221).

[0106] Referring to FIG. 5, the rotation shaft (130) according to the present embodiment may include a drive shaft portion (131), a first impeller shaft portion (132), and a second impeller shaft portion (133).

[0107] The drive shaft portion (131) may be formed in a cylindrical shape and may be rotatably installed inside the stator (121). For example, the length of the drive shaft portion (131) may be formed to be longer than or equal to the axial length of the stator (121), and the axial center of the drive shaft portion (131) may be coupled to be positioned radially on the same line as the axial center of the stator (121).

[0108] The first impeller shaft portion (132) may be extended or assembled as a single body from one end of the drive shaft portion (131), and the second impeller shaft portion (133) may be extended or assembled as a single body from one end of the drive shaft portion (131). In this embodiment, an example is shown in which the first impeller shaft portion (132) and the second impeller shaft portion (133) are extended as a single body from both ends of the drive shaft portion (131).

[0109] A thrust runner (1324) that is axially supported by a first thrust bearing (146) and a second thrust bearing (147) to be described later may be formed on the first impeller shaft portion (1322). For example, the thrust runner (1324) may be formed in a disk shape by extending radially from the outer circumferential surface of the first bearing surface portion (1322).

[0110] Referring to FIGS. 4 and 5, the thrust runner (1324) may be provided between the first bearing shell (143) and the bearing support member (1115) and may be axially supported. In other words, the thrust runner (1324) may form a movable side support member, and the first bearing shell (143) and the bearing support member (1115) may each form a fixed side support member. Accordingly, the rotation shaft (130) may be axially supported on both sides together with the first impeller (151) and the second impeller (161) coupled to both ends of the rotation shaft (130).

[0111] The thrust runner (1324) may be formed so that its outer circumference is spaced apart from the inner circumference of the first space (1114a). The outer diameter of the thrust runner (1324) may be formed smaller than the inner diameter of the first space (1114a). Although not shown in the drawing, coolant may be supplied to the first thrust bearing (146) and the second thrust bearing (147) through a coolant supply unit (not shown), and in this case, the coolant moves toward the driving motor (120).

[0112] As illustrated in FIGS. 4 and 5, the first thrust bearing (146) may be provided on a first side (not shown) of the thrust runner (1324) facing the first impeller (151). The second thrust bearing (147) may be provided on a second side (not shown) of the thrust runner (1324) facing the electric part. In this case, since both the first thrust bearing (146) and the second thrust bearing (147) are installed on the rotation shaft (130), the installation and assembly of the first thrust bearing (146) and the second thrust bearing (147) may be easy.

[0113] The second impeller shaft portion (133) may be inserted and fixed into the second compression portion (160) side end (hereinafter referred to as the second end) of the drive shaft portion (131). For example, the second impeller shaft portion (133) may be welded and joined in a press-fit state to the second end of the drive shaft portion (131), similar to the first impeller shaft portion (132).

[0114] The second impeller shaft portion (133) is formed symmetrically with respect to the first impeller shaft portion (132) and the drive shaft portion (131), but since the second bearing portion (142) is not provided with a thrust bearing, a thrust runner (not shown) may be excluded. However, in some cases, the second bearing portion (142) may also be provided with a thrust bearing, and the second impeller shaft portion (133) may be provided with a thrust runner (not shown).

[0115] Fig. 6 is a cross-sectional view showing the first flow path (1125d) in the first impeller housing (110), and Fig. 7 is a cross-sectional view showing the angle of the expansion tube adjusted in the first impeller housing (110) of Fig. 6.

[0116] Below, the detailed configuration of the first to third euros (1125d, 1115d, 1136a) will be described.

[0117] The first impeller housing (110) may be provided with a first flow path receiving projection (1125) that protrudes from one surface of the exterior and has a first flow path (1125d) provided therein.

[0118] The first guiding member (1125) is provided on the upper side (112b) of the first suction port (1121) of the first impeller housing (110) in Fig. 2, where it is shown. In Fig. 2, the side (112b) may be the left side.

[0119] For example, the first flow passage accommodating portion (1125) may be formed integrally with the first impeller housing (110). Since the first flow passage accommodating portion (1125) is formed integrally with the first impeller housing (110), compared to a structure in which a separate pipe is installed in the existing first impeller housing (110), installation of a gasket and bolts is not required, thereby reducing manufacturing and maintenance costs.

[0120] The second impeller housing (113) may be provided with a third flow path receiving projection (1136) that protrudes from one surface of the exterior and has a third flow path (1136a) provided therein.

[0121] The third flow passage receiving portion (1136) is provided on one side (113b) of the second suction port (1131) of the second impeller housing (113) shown in FIGS. 3 and 5. In FIG. 3, the one side (113b) may be the left side. Referring to FIG. 5, the outlet-side end of the third flow passage receiving portion (1136) may be connected to the inlet side of the second suction port (1131) of the second impeller housing (113). As shown in FIG. 3, the outlet-side end of the third flow passage receiving portion (1136) may be coupled to the center of the second impeller housing (113).

[0122] For example, the third flow passage accommodating portion (1136) may be formed integrally with the second impeller housing (113). Since the third flow passage accommodating portion (1136) is formed integrally with the second impeller housing (113), compared to a structure in which a separate pipe is installed in the existing second impeller housing (113), installation of a gasket and bolts is not required, thereby reducing manufacturing and maintenance costs.

[0123] The motor housing (110) may be provided with a second flow path receiving projection (1113) that protrudes from the outer periphery and has a second flow path (1115d) provided therein.

[0124] For example, the second flow passage accommodating portion (1113) may be formed integrally with the motor housing (110). Since the second flow passage accommodating portion (1113) is formed integrally with the motor housing (110), the size of the motor housing (110) in the lateral direction can be reduced compared to a structure in which a separate pipe is arranged on the side of the existing motor housing (110), thereby enabling the packaging area to be reduced compared to the existing turbo compressor (10).

[0125] Referring to FIGS. 2 and 3, an example is shown in which a first flow passage accommodating protrusion (1125) is provided on one surface of a first impeller housing (110) visible in the drawings. The first flow passage accommodating protrusion (1125) is spaced apart from the center of the first impeller housing (110) in which the first suction port (1121) is provided by a predetermined distance. This is because the refrigerant that is introduced into the first impeller (151) near the center of the first impeller housing (110) and compressed flows out through the first flow passage accommodating protrusion (1125) from the side of the first impeller housing (110).

[0126] On the other hand, one end of the third flow passage receiving member (1136) on the outlet side is connected to the center of the second impeller housing (113). This is because the refrigerant compressed in the first impeller (151) flows through the flow path inside the third flow passage receiving member (1136) and flows into the second impeller (161) from the center of the second impeller housing (113).

[0127] In addition, as illustrated in FIGS. 2 to 5, the motor housing (110) is provided with a second flow passage protrusion (1113) between the first flow passage protrusion (1125) and the third flow passage protrusion (1136). The second flow passage protrusion (1113) is connected to the first flow passage protrusion (1125) and the third flow passage protrusion (1136), respectively, so that the refrigerant compressed in the first impeller (151) and passing through the first flow passage protrusion (1125) can be supplied to the third flow passage protrusion (1136).

[0128] For example, as illustrated in Fig. 3, the second accommodating protrusion (1113) may be in contact from one end to the other so as not to have a space separated from the motor housing (110). However, the present invention is not necessarily limited to this structure.

[0129] The second euro-accommodating protrusion (1113) can extend in the extension direction of the rotation axis (i.e., axial direction).

[0130] The ends of the first flow passage receiving portion (1125) and the third flow passage receiving portion (1136) may be arranged parallel to each other. The ends of the first flow passage receiving portion (1125) and the third flow passage receiving portion (1136) may each be provided with a first flange portion (1125c, 1136e).

[0131] At both ends of the second flow passage accommodating portion (1113), a second flange portion (1113c) may be provided so as to be sealedly connected to the first flange portions (1125c, 1136e) provided at the ends of the first flow passage accommodating portion (1125) and the third flow passage accommodating portion (1136), respectively.

[0132] The first flange portion (1125c) may be formed to protrude laterally, i.e., in the radial direction of the flow path, from the end of the first flow path receiving portion (1125). Accordingly, it may have a larger diameter than the first flow path receiving portion (1125).

[0133] The second flange portion (1113c), like the first flange portion (1125c, 1136e), may be formed to protrude laterally, i.e., in the radial direction of the flow path, from the end of the second flow path-accommodating protrusion (1113). The second flange portion (1113c) may have a larger diameter than the second flow path-accommodating protrusion (1113).

[0134] By means of the first and second flange portions (1125c, 1136e, 1113c), the assembly between the first to third flow passage accommodating portions (1125, 1113, 1136) can be improved. In addition, a flow path can be provided through which the refrigerant discharged from the first impeller (151) can flow toward the second impeller (161) without causing refrigerant leakage between the first to third flow passage accommodating portions (1125, 1113, 1136).

[0135] For example, the first flange portion (1125c, 1136e) and the second flange portion (1113c) can be connected to each other by bolting. To this end, the first flange portion (1125c, 1136e) and the second flange portion (1113c) can be provided with a plurality of holes formed to be in communication with each other. Bolts are connected to the plurality of holes of the first flange portion (1125c, 1136e) and the second flange portion (1113c), so that the first flange portion (1125c, 1136e) and the second flange portion (1113c) can be connected to each other.

[0136] Referring to FIGS. 5 to 7, the first euro-accommodating protrusion (1125) may include a first portion (1125a) and a second portion (1125b).

[0137] The first portion (1125a) can extend in a direction intersecting one surface of the exterior of the first impeller housing (110) with one surface of the exterior of the first impeller housing (110).

[0138] The second part (1125b) may be formed into a curved surface, extending from the end of the first part (1125a).

[0139] In Fig. 6, an example is shown in which the first part (1125a) extends in an upper right direction from the upper side of the first impeller housing (110) based on the drawing. In addition, an example is shown in which the second part (1125b) is formed as a downward curved surface from the end of the first part (1125a).

[0140] In the present invention, since the first impeller housing (110) does not allow the discharged refrigerant to flow through a conventional separate pipe, and the first flow path receiving projection (1125) is provided on one side of the first impeller housing (110), the distance through which the discharged refrigerant flows is reduced, so that the flow loss can be reduced.

[0141] In addition, the first part (1125a) and the second part (1125b) provided in the first flow passage (1125) can secure an expansion distance to allow the refrigerant discharged from the first impeller (151) to flow. Depending on the position or angle at which the first part (1125a) and the second part (1125b) are formed, the pressure loss in the inner flow passages of the first part (1125a) and the second part (1125b) can vary.

[0142] In particular, a discharge path is provided on the inside of the first part (1125a) and the second part (1125b), and by adjusting the angle at which the discharge path is expanded, the pressure loss of the path can also be reduced.

[0143] The angle at which the discharge path formed by the first part (1125a) and the second part (1125b) is expanded is described.

[0144] The first angle formed by the first part (1125a) and the extension line extending from the outer surface of the first impeller housing (110) may be 5 degrees or more and 15 degrees or less. Fig. 7 illustrates an example in which the first angle is formed to be approximately 15 degrees.

[0145] The present invention forms an integrated flow path in the first impeller housing (110), the second impeller housing (113), and the motor housing (110) without requiring separate piping as in the past, thereby reducing pressure loss by 42% compared to the existing flow path.

[0146] Referring to FIGS. 6 and 7, the first impeller housing (110) may include a first flow wall portion (1125e) and a second flow wall portion (1125f).

[0147] The first flow wall portion (1125e) is provided on the inside of the first impeller housing (110) and can be formed parallel to the first portion (1125a).

[0148] The second flow wall portion (1125f) is connected to intersect the first flow wall portion (1125e) and can be spaced apart from the second portion (1125b).

[0149] The first flow path wall (1125e) may include a first surface (1125e1) provided adjacent to the first impeller (151) side, and a second surface (1125e2) provided on the first flow path (1125d) side, which forms a surface different from the first surface (1125e1).

[0150] The first euro (1125d) may have a portion in which the cross-sectional area gradually increases between the first portion (1125a) and the first euro wall portion (1125e).

[0151] The first surface (1125e1) and the second surface (1125e2) can form a predetermined second angle with each other. In Fig. 7, the second angle is represented as θ''.

[0152] As described above, the first angle is the angle formed between the first portion (1125a) and an extension line extending from an outer surface of the first impeller housing (110). The first angle may be greater than the second angle. Furthermore, the first angle may be less than 15 degrees. In Fig. 7, the first angle is depicted as θ'.

[0153] The third flow path (1136a) can be formed in a shape that is folded at least twice. Referring to FIG. 5, an example in which the third flow path (1136a) is formed in a shape that is folded twice is illustrated.

[0154] The third euro-accommodating protrusion (1136) may include first to third suction protrusions (1136b, 1136c, 1136d).

[0155] The first suction protrusion (1136b) can be connected to the second flow passage protrusion (1113) and formed parallel to the second flow passage protrusion (1113).

[0156] The second suction protrusion (1136c) may be provided to be connected to the suction port of the second impeller (161).

[0157] The third suction protrusion (1136d) may be provided to be connected between the first suction protrusion (1136b) and the second suction protrusion (1136c).

[0158] The third flow passage protrusion (1136) is configured to include the first to third suction protrusions (1136b, 1136c, 1136d), so that the compressed refrigerant flowing in through the second flow passage protrusion (1113) can be provided to the second suction port (1131) of the second compression unit (160) with minimal pressure drop.

[0159] Figure 8 is a conceptual diagram showing the analysis results of turbulence concentration when an existing euro, an integral euro, and an integral euro with an improved angle of the expanded pipe are applied.

[0160] In the existing path where separate piping is applied, the angle of the expansion pipe through which the path discharged from the first impeller (151) flows is 14.4 degrees. In the path where separate piping is applied where the angle of the expansion pipe is 14.4 degrees, it was confirmed that the path discharged from the first impeller (151) has a turbulent intensity value of approximately 420% in some parts near the expansion pipe.

[0161] In addition, in the integrated flow path of the present invention, an example is shown in which the angle of the expansion pipe through which the flow path discharged from the first impeller (151) flows is 20 degrees. In the integrated flow path having the angle of the expansion pipe of 20 degrees, it was confirmed that the flow path discharged from the first impeller (151) has a flow path in which the turbulent intensity value near the expansion pipe is approximately 630%.

[0162] In addition, in the integrated flow path of the present invention, an example is shown in which the angle of the expansion pipe through which the flow path discharged from the first impeller (151) flows is 12.6 degrees. In the integrated flow path having the angle of the expansion pipe of 12.6 degrees, it was confirmed that the flow path discharged from the first impeller (151) has a very small portion of the flow path in which the turbulent intensity value near the expansion pipe is approximately 420%.

[0163] FIG. 9 is a graph showing the pressure loss in the first to third flow paths (1125d, 1115d, 1136a) of the first impeller housing (110) and the second impeller housing (113) according to the euro shape.

[0164] In the existing Euro with separate piping applied, the refrigerant discharged from the first impeller (151) is 7.8 kgf / cm 2 Approximately 7.73 kgf / cm at a length of 200 mm from the pressure 2 This causes pressure loss.

[0165] In the integrated flow path of the present invention, where the angle of the expansion tube is 20 degrees, the refrigerant discharged from the first impeller (151) is 7.8 kgf / cm 2 Approximately 7.61 kgf / cm at a length of 150 mm from the pressure 2 This causes pressure loss.

[0166] In the integrated flow path of the present invention, where the angle of the expansion tube is 12.6 degrees, the refrigerant discharged from the first impeller (151) is 7.8 kgf / cm 2 Approximately 7.76 kgf / cm at a length of 200 mm from the pressure 2 This causes pressure loss.

[0167] In this way, when applying an integrated euro and maintaining the angle of the expansion pipe at approximately 12.6 degrees, less pressure loss occurs than in a conventional euro with separate piping applied.

[0168] Referring to FIGS. 4 and 5, the first compression unit (150) according to the present embodiment may include a first impeller (151), a first diffuser (1123), and a first volute (1124). However, among the components forming the first compression unit (150), the first diffuser (1123) and the first volute (1124) are as described above with respect to the first impeller housing (112). That is, the first diffuser (1123) is formed between the first impeller housing (112) and the first bearing shell (143), and the first volute (1124) may be formed in the first impeller housing (112).

[0169] As described above, the first impeller (151) forms a first compression unit (150), which is functionally a single-stage compression unit, together with the first diffuser (1123) and the first volute (1124). Accordingly, the suction side of the first impeller (151) can be connected to the refrigerant suction pipe (115), and the discharge side of the first impeller (151) can be connected to the suction side of the second impeller (161), which forms part of the two-stage compression unit (second compression unit (160)), through the first to third flow paths (1125d, 1115d, 1136a).

[0170] In particular, the present invention provides the first to third flow paths (1125d, 1115d, 1136a) on the inside of the housing (110), thereby reducing the packaging area and reducing the number of parts used, such as gaskets or O-rings, compared to the conventional method.

[0171] Referring to FIGS. 4 and 5, the second compression unit (160) according to the present embodiment may include a second impeller (161), a second diffuser (1133), and a second volute (1134). However, among the components forming the second compression unit (160), the second diffuser (1133) and the second volute (1134) are as described above with respect to the second impeller housing (113). That is, the second diffuser (1133) is formed between the second impeller housing (113) and the second bearing shell (144), and the second volute (1134) may be formed in the second impeller housing (113).

[0172] As previously described, the second impeller (161) forms a functional two-stage compression unit together with the second diffuser (1133) and the second volute (1134). Accordingly, the suction side of the second impeller (161) can be connected to the discharge side of the first impeller (151) via a refrigerant connection pipe (116), and the discharge side of the second impeller (161) can be connected to the inlet side of the condenser (20) via a refrigerant discharge pipe (117).

[0173] The overall shape of the second impeller (161) may be formed to be almost identical to that of the first impeller (151). However, the diameter of the second impeller (161) may be formed to be smaller than that of the first impeller (151). The shape of the second impeller (161) is replaced with the description of the first impeller (151).

[0174] The turbo compressor (10) according to the above embodiment operates as follows.

[0175] That is, when power is applied to the electric motor (120), rotational force is generated by the induced current between the stator (121) and the rotor (122), and the rotational force causes the rotational shaft (130) to rotate together with the rotor (122).

[0176] Then, the rotational power of the electric motor (120) is transmitted to the first impeller (151) and the second impeller (161) by the rotation shaft (130), and the first impeller (151) and the second impeller (161) rotate simultaneously in their respective impeller receiving spaces (1122)(1132).

[0177] Then, the refrigerant that has passed through the evaporator (40) of the refrigeration cycle device flows into the first impeller (151) receiving space (1122) through the refrigerant suction pipe (115) and the first suction port (1121), and the refrigerant moves while rotating along the first impeller (151), increasing the static pressure and simultaneously passing through the first diffuser (1123) with centrifugal force.

[0178] Then, the refrigerant passing through the first diffuser (1123) has kinetic energy due to centrifugal force in the first diffuser (1123) leading to an increase in the pressure head, and the centrifugally compressed high-temperature, high-pressure refrigerant is collected in the first volute (1124) and discharged from the first compression unit (150).

[0179] The refrigerant compressed in the first compression unit (150) is guided to the second suction port (1131) through the first flow path (1125d) provided inside the first impeller housing (110), the second flow path (1115d) of the motor housing (110), and the third flow path (1136a) provided inside the second impeller housing (113).

[0180] Unlike the prior art, in the present invention, the refrigerant discharged from the first compression unit (150) is not guided to the second suction port (1131) of the second impeller housing (113) forming the second compression unit (160) through a separate refrigerant connection pipe.

[0181] On the other hand, in the present invention, the refrigerant discharged from the first compression unit (150) is guided to the second suction port (1131) of the second impeller housing (113) through the first to third flow paths (1125d, 1115d, 1136a) provided inside the housing (110).

[0182] As this refrigerant rotates along the second impeller (161), the static pressure increases again and at the same time, it passes through the second diffuser (1133) with centrifugal force.

[0183] Then, the refrigerant passing through the second diffuser (1133) is compressed to the desired pressure by centrifugal force, and this two-stage compressed high-temperature, high-pressure refrigerant is collected in the second volute (1134) and discharged to the condenser (20) through the second discharge port (1135) and the refrigerant discharge pipe (117), repeating a series of processes.

[0184] The turbo compressor (10) of the present invention can reduce the overall size by providing the first to third flow paths (1125d, 1115d, 1136a) in the housing (110) compared to a structure using existing separate piping, so that the packaging area can be reduced compared to the existing turbo compressor (10).

[0185] In addition, the turbo compressor (10) of the present invention changes the method of fixing the first and second stage shells by integrating the first to third flow paths (1125d, 1115d, 1136a) into the housing (110) and the volute, and reduces the number of parts used, such as gaskets or O-rings, compared to the existing ones, by using a structure in which the volute surrounds them.

[0186] The present invention can improve the assembly between the first to third flow path receiving protrusions (1125, 1113, 1136) by the first and second flange portions (1125c, 1136e, 1113c). In addition, it is possible to provide a flow path through which the refrigerant discharged from the first impeller (151) can flow toward the second impeller (161) without causing refrigerant leakage between the first to third flow path receiving protrusions (1125, 1113, 1136).

[0187] The turbo compressor (10) described above is not limited to the configuration and method of the embodiments described above, and the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

[0188] It will be apparent to those skilled in the art that the present invention may be embodied in other specific forms without departing from the spirit and essential characteristics thereof. Therefore, the above detailed description should not be construed in any way as limiting but rather as illustrative. The scope of the present invention should be determined by a reasonable interpretation of the appended claims, and all modifications within the scope of equivalents of the present invention are intended to be included within the scope of the present invention.

[0189] The present invention can be used in a turbocompressor that enables compact packaging while reducing the number of parts without increasing the loss of the conventional turbocompressor compared to the conventional turbocompressor.

Claims

1. Motor housing having a motor room; A driving motor installed in the above motor room to generate rotational force; A rotary shaft that transmits the rotational power of the above driving motor; First and second impellers, respectively coupled to both sides of the above rotating shaft and compressing the sucked refrigerant; and It includes first and second impeller housings that accommodate the first and second impellers so as to be rotatable, respectively. On one side of the first impeller housing, a first flow path is provided to allow the refrigerant compressed in the first impeller to flow. The above motor housing is provided with a second passage that is connected to the first passage and provides the compressed refrigerant to the second impeller housing. A turbo compressor having a third flow path on one side of the second impeller housing, which is connected to the second flow path and enables the compressed refrigerant to be supplied to the suction port of the second impeller.

2. In paragraph 1, A turbo compressor in which the first impeller housing is provided with a first flow path receiving projection that protrudes from one surface of the exterior and has the first flow path provided therein.

3. In paragraph 2, The above first euro-receiving portion is, A first portion extending in a direction intersecting one surface of the exterior of the first impeller housing; and A turbocompressor comprising a second portion extending from an end of the first portion and formed into a curved surface.

4. In paragraph 3, A turbo compressor wherein a first angle formed by an extension line extending from the first part to the outer surface of the first impeller housing is 5 degrees or more and 15 degrees or less.

5. In paragraph 3, The above first impeller housing, A first flow path wall portion provided on the inside of the first impeller housing and formed parallel to the first portion; and A turbocompressor comprising a second flow wall portion connected to the first flow wall portion so as to intersect with the second portion and spaced apart from the second portion.

6. In paragraph 5, A turbo compressor in which the first flow path is formed so that the cross-sectional area gradually increases between the first section and the first flow path wall.

7. In paragraph 5, The first Euro Wall is, A turbo compressor comprising a first surface provided adjacent to the first impeller side, and a second surface formed different from the first surface but provided on the first flow path side.

8. In paragraph 7, The first and second surfaces are formed to form a predetermined second angle with respect to each other, A turbo compressor in which a first angle formed by an extension line extending from the first part to the outer surface of the first impeller housing is greater than a second angle.

9. In paragraph 2, A turbo compressor having a second flow path receiving projection formed protruding from the outer periphery of the above motor housing and having the second flow path provided therein.

10. In paragraph 9, A turbo compressor in which the second euro-shoe vortex and the motor housing are formed to be in contact from one end to the other without providing a space therebetween.

11. In paragraph 9, The ends of the first flow-through receptacle and the third flow-through receptacle are arranged parallel to each other, and the ends of the first flow-through receptacle and the third flow-through receptacle are each provided with a first flange portion. A turbo compressor having a second flange portion provided at both ends of the second euro receiving portion so as to be sealedly connected to the first flange portion.

12. In paragraph 9, A turbo compressor in which the second axial receptacle is provided to extend along the axial direction in which the rotation shaft extends.

13. In paragraph 9, A turbo compressor in which the second impeller housing is provided with a third flow path receiving projection formed protruding from one surface of the exterior and having the third flow path provided therein.

14. In paragraph 1, A turbo compressor in which the first flow path is provided inside the first impeller housing, the second flow path is provided inside the motor housing, and the third flow path is provided inside the second impeller housing.

15. In paragraph 13, The above third euro is, A turbo compressor formed into a shape that is bent at least twice.

16. In paragraph 13, The above third euro receptacle is, A first suction protrusion connected to the second flow path receiving protrusion and formed parallel to the second flow path receiving protrusion; A second suction projection provided to be connected to the suction port of the second impeller; and A turbo compressor including a third suction projection portion provided to be connected between the first suction projection portion and the second suction projection portion.

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