Scroll compressor

Abstract

Scroll compressor, featuring: a case (100); a motor (200) provided in the housing (100); a rotating shaft (300) turned by the motor (200); a spiral winding (400) moved in a circular motion by the rotating shaft (300); and a stationary spiral (500) which together with the rotating spiral (400) forms a compression chamber (C), where the housing (100) has: a central housing (110) through which the rotating shaft (300) passes; a front housing (120) forming a motor mounting space (S1) in which the motor (200) is mounted; and a rear housing (130) comprising a discharge chamber (D) which receives a refrigerant discharged from the compression chamber (C), a discharge port (131) which directs the refrigerant from the discharge chamber (D) to the outside of the housing (100), an inlet port (133) into which a medium-pressure refrigerant is introduced from outside the housing (100), and an inlet chamber (I) which receives the refrigerant introduced through the inlet port (133), wherein at least part of the inlet chamber (I) is designed such that it is received in the ejection chamber (D), and wherein the stationary spiral (500) has an injection hole (514) which directs the refrigerant from the inlet chamber (I) to the compression chamber (C), wherein the rear housing (130) is integrally formed, and the rear housing (130) has: a first annular wall (134) located on the outermost side in the radial direction of the rear housing (130); a second annular wall (136) which is incorporated in the radial direction of the rear housing (130) in the first annular wall (134) and forms the ejection chamber (D); and a third annular wall (138) which is received in the radial direction of the rear housing (130) in the second annular wall (136) and forms the inlet chamber (I).

Description

[0001] The present invention relates to a scroll compressor, and in particular a scroll compressor that can compress a refrigerant with a stationary spiral and a rotating spiral.

[0002] A vehicle is generally equipped with an air conditioning system (A / C) for heating and cooling the interior. The air conditioning system is a component of a cooling system and includes a compressor that compresses a gaseous, low-temperature, low-pressure refrigerant from a compressor to a gaseous, high-temperature, high-pressure refrigerant and directs it to a condenser.

[0003] The compressor comprises oscillating compression of a refrigerant by the reciprocating movement of a piston and rotary compression during rotation. According to a power transmission method, the oscillating type includes a crank type, which transmits power to a plurality of pistons by means of a crank, a swashplate type, which transmits power to a rotating shaft on which a swashplate is installed, and the like, and wherein the rotary type comprises a blade rotary type, which uses a rotating shaft and blades, and a scroll type, which uses a rotating spiral and a stationary spiral.

[0004] Due to its advantages, namely that it achieves a relatively high compression ratio compared to other types of compressors and maintains a stable torque through smooth refrigerant intake, compression and discharge strokes, a scroll compressor is widely used in refrigerant compression in air conditioning systems.

[0005] Fig. Figure 1 is a cross-sectional view showing a conventional scroll compressor.

[0006] Referring to Fig. 1 A conventional scroll compressor comprises a housing 100, a motor 200 provided in the housing, a rotating shaft 300 turned by the motor 200, a rotating spiral 400 moved by the rotating shaft 300 and a stationary spiral 500 which forms a compression chamber C with the rotating spiral 400.

[0007] In the conventional scroll compressor according to this configuration, when current is applied to the motor 200, the rotating shaft 300 rotates together with a rotor of the motor 200, and the spiral 400 is moved around by the rotating shaft 300, and the refrigerant is drawn into the compression chamber C, compressed in the compression chamber C, and discharged from the compression chamber C by the circular motion of the spiral 400.

[0008] However, in the conventional scroll compressor, a certain amount of refrigerant ejected from the compression chamber C is fixed, and improvements in the compressor's performance and efficiency are limited.

[0009] Similar compressors are known from DE 10 2015 100 112 A1, DE 10 2017 122 327 A1, US 2009 / 0028736 A1 and DE 10 2019 107 943 A1.

[0010] Therefore, an object of the present invention is to provide a scroll compressor that can improve the performance and efficiency of the compressor by increasing the amount of refrigerant discharged from a compression chamber.

[0011] To solve the problem described above, the present invention provides a scroll compressor comprising a housing; a motor provided in the housing; a rotating shaft turned by the motor; a spiral spiral moved around the rotating shaft; and a stationary spiral spiral which, together with the spiral spiral spiral, forms a compression chamber, wherein the housing comprises a central housing through which the rotating shaft passes; a front housing which forms a motor receiving chamber in which the motor is received;and a rear housing comprising a discharge chamber in which a refrigerant discharged from the compression chamber is received, a discharge port which directs the refrigerant from the discharge chamber to the outside of the housing, an inlet port into which a medium-pressure refrigerant is introduced from outside the housing, and an inlet chamber which receives the refrigerant introduced through the inlet port, wherein the stationary spiral has an injection port which directs the refrigerant from the inlet chamber to the compression chamber.

[0012] The rear housing can be integrally formed.

[0013] At least part of the inlet chamber can be formed to be received into the ejection chamber.

[0014] The rear housing 130 can have a first annular wall coupled to the central housing and forming a spiral receiving chamber in which the rotating spiral and the stationary spiral are received; a second annular wall received in the first annular wall and forming the ejection chamber; and a third annular wall received in the second annular wall and forming the inlet chamber.

[0015] The first ring-shaped wall, the second ring-shaped wall, and the third ring-shaped wall can have different heights.

[0016] The second annular wall is formed in contact with an outer circumference of a fixed base plate of the fixed spiral, and the second annular wall can press the fixed spiral towards the central housing when the rear housing is coupled to the central housing.

[0017] The third ring-shaped wall can be formed to be spaced apart from the stationary spiral.

[0018] An injection valve assembly, which communicates and blocks between the inlet chamber and the injection hole, can be formed on an end surface of the third annular wall.

[0019] The injector assembly may include a cover plate having an inlet that communicates with and covers the inlet chamber; an injector that opens and closes the inlet; and a valve plate having a beveled space that acts as a holder for the injector and receives the refrigerant flowing in through the inlet, and an outlet that directs the refrigerant in the beveled space to the injection orifice.

[0020] The stationary spiral includes an exhaust port that expels the refrigerant from the compression chamber into the exhaust chamber, and an exhaust valve may be formed between the injection valve assembly and the stationary spiral, which opens and closes the exhaust port.

[0021] The refrigerant directed to the injection hole can exchange heat with the refrigerant in the discharge chamber through the third annular wall and the injection valve assembly.

[0022] At least part of the ejection opening can be formed to be received in the inlet chamber.

[0023] The refrigerant in the inlet chamber can exchange heat with the refrigerant in the outlet opening through a wall of the outlet opening located in the inlet chamber.

[0024] At least part of the inlet opening can be formed to be received in the ejection chamber.

[0025] The refrigerant in the inlet opening can exchange heat with the refrigerant in the discharge chamber through a wall of the inlet opening located in the discharge chamber.

[0026] The scroll compressor according to the invention comprises a housing; a motor provided in the housing; a rotating shaft turned by the motor; a spiral spiral moved around the rotating shaft; and a stationary spiral which, together with the spiral spiral, forms a compression chamber, wherein the housing comprises a central housing through which the rotating shaft passes; a front housing which forms a motor receiving space in which the motor is received;and a rear casing comprising a discharge chamber which receives refrigerant discharged from the compression chamber, a discharge port which directs the refrigerant from the discharge chamber to the outside of the casing, an inlet port into which a medium-pressure refrigerant is introduced from outside the casing, and an inlet chamber which receives the refrigerant introduced through the inlet port, wherein the stationary coil has an injection port which directs the refrigerant from the inlet chamber to the compression chamber, thereby increasing the quantity of refrigerant discharged from the compression chamber and improving the performance and efficiency of the compressor. Fig. Figure 1 is a cross-sectional view representing a conventional scroll compressor. Fig. Figure 2 is a cross-sectional view showing a scroll compressor according to an embodiment of the invention. Fig. Figure 3 is a cross-sectional view showing a rear case side of the scroll compressor. Fig. 2 represents from a different direction, Fig. Figure 4 is an enlarged cross-sectional view of part A of Fig. 3, Fig. Figure 5 is a front view showing the rear housing of the scroll compressor. Fig. 2 represents, Fig. 6 is a rear view of Fig. 5, Fig. 7 is a perspective view of Fig. 6, Fig. Figure 8 is an exploded perspective view taken inside the rear case of Fig. 7 recorded parts, Fig. Figure 9 is an exploded perspective view showing an injector assembly of parts from Fig. 8 represents, Fig. Figure 10 is a perspective view showing a rear surface of a cover plate of the injection valve brewing unit. Fig. 9 represents, Fig. Figure 11 is a perspective view showing a rear surface of a valve plate of the injection valve brewing unit. Fig. 9 represents, Fig. 12 is a perspective view, taken along line II of Fig. 9, Fig. Figure 13 is a front view showing a fixed spiral and an ejection valve below the parts of Fig. 8 represents, Fig. 14 is a rear view of Fig. 13, Fig. 15 is a perspective view, taken along line II-II of Fig. 13, Fig. Figure 16 is a cross-sectional view showing a fixed casing, a circumferential casing, and an injection hole, where a rotation angle of a rotating shaft is a first angle to describe the opening and closing process of the injection hole. Fig. 13 to explain, Fig. Figure 17 is a cross-sectional view showing a fixed casing, a circumferential casing, and an injection hole, where a rotation angle of a rotating shaft is a second angle to describe the opening and closing process of the injection hole. Fig. 13 to explain, Fig. Figure 18 is a cross-sectional view showing a fixed casing, a circumferential casing, and an injection hole, where a rotation angle of a rotating shaft is a third angle to describe the opening and closing process of the injection hole. Fig. 13 to explain, Fig. Figure 19 is a cross-sectional view showing a fixed casing, a circumferential casing, and an injection hole, where a rotation angle of a rotating shaft is a fourth angle to describe the opening and closing process of the injection hole. Fig. 13 to explain, Fig. 20 is a scheme that describes the timing of the opening and closing of the injection hole of Fig. 13 represents, Fig. Figure 21 is an exploded perspective view showing an injection valve assembly in a scroll compressor according to another embodiment of the invention. Fig. 22 is a top view showing an injector and valve plate of Fig. 21 represents, Fig. 23 is a cross-sectional view, taken along line III-III of Fig. 22, and Fig. 24 is a cross-sectional view, taken along line IV-IV of Fig. 22.

[0027] A scroll compressor according to the invention is described in more detail below with reference to the accompanying drawings.

[0028] Fig. Figure 2 is a cross-sectional view showing a scroll compressor according to an embodiment of the invention. Fig. Figure 3 is a cross-sectional view showing a rear case side of the scroll compressor. Fig. 2 represents from a different direction, Fig. Figure 4 is an enlarged cross-sectional view of part A of Fig. 3, Fig. Figure 5 is a front view showing the rear housing of the scroll compressor. Fig. 2 represents, Fig. 6 is a rear view of Fig. 5, Fig. 7 is a perspective view showing a portion of the rear casing that has been cut away, as a perspective view from Fig. 6 represents, Fig. Figure 8 is an exploded perspective view taken inside the rear case of Fig. 7 recorded parts, Fig. Figure 9 is an exploded perspective view showing an injector assembly of parts from Fig. 8 represents, Fig. Figure 10 is a perspective view showing a rear surface of a cover plate of the injection valve brewing unit. Fig. 9 represents, Fig. Figure 11 is a perspective view showing a rear surface of a valve plate of the injection valve brewing unit. Fig. 9 represents, Fig. 12 is a perspective view, taken along line II of Fig. 9, Fig. Figure 13 is a front view showing a fixed spiral and an ejection valve below the parts of Fig. 8 represents, Fig. 14 is a rear view of Fig. 13 and Fig. 15 is a perspective view, taken along line II-II of Fig. 13.

[0029] Furthermore, the Fig. 16, Fig. 17, Fig. 18 to Fig. 19 cross-sectional views showing the opening and closing process of the injection hole of Fig. 13. Explain; in particular, Fig. 16 a cross-sectional view showing a fixed casing, a circumferential casing and an injection hole, where a rotation angle of a rotating shaft is a first angle, Fig. Figure 17 is a cross-sectional view showing a fixed casing, a circumferential casing and an injection hole, where a rotation angle of a rotating shaft is a second angle. Fig. Figure 18 is a cross-sectional view showing a fixed casing, a circumferential casing, and an injection hole, where a rotation angle of a rotating shaft is a third angle, and Fig. Figure 19 is a cross-sectional view showing a fixed casing, a circumferential casing and an injection hole, where a rotation angle of a rotating shaft is a fourth angle.

[0030] Furthermore, Fig. 20 a scheme showing the timing of the opening and closing of the injection hole of Fig. 13 represents.

[0031] Referring to the Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 11, Fig. 12, Fig. 13, Fig. 14, Fig. 15, Fig. 16, Fig. 17, Fig. 18, Fig. 19 to Fig. 20 A scroll compressor according to an embodiment of the invention can have a housing 100, a motor 200 provided in the housing 100, a rotating shaft 300 turned by the motor 200, a spiral 400 moved around the rotating shaft 300 and a stationary spiral 500 which forms a compression chamber C with the spiral 400.

[0032] The scroll compressor according to this embodiment can further have an injection flow path for directing the medium-pressure refrigerant from outside the housing 100 (in a vapor compression refrigeration circuit comprising a scroll compressor, a condenser, an expansion valve and an evaporator, for example downstream of the condenser) into the compression chamber C, as well as an injection valve assembly 700 for opening and closing the injection flow path.

[0033] Here, the injection flow path is formed such that it extends from a rear housing 130 to the stationary spiral 500 by including an inlet opening 133, an inlet chamber I, an inlet 712, a chamfered space 734, a connecting flow path 738, an outlet 736 and an injection hole 514, which will be described later, and the injection valve assembly 700 can be arranged between the rear housing 130 and the stationary spiral 500 by including an inlet 712, a chamfered space 734, a connecting flow path 738 and an outlet 736, which will be described later.

[0034] In particular, the housing can be 100, as in Fig. Figure 2 shows a central housing 110 through which the rotating shaft 300 passes, a front housing 120 which together with the central housing 110 forms a motor receiving chamber S1 in which the motor 200 is received, and a rear housing 130 which together with the central housing 110 forms a spiral receiving chamber S2 in which the rotating spiral 400 and the stationary spiral 500 are received.

[0035] The central housing 110 can have a central base plate 112, which divides the motor receiving chamber S1 and the spiral receiving chamber S2 and supports the rotating spiral 400 and the stationary spiral 500, as well as a central side plate 114, which projects from an outer circumference of the central base plate 112 to the front housing 120.

[0036] The central base plate 112 is formed in an essentially circular plate shape, and in the center of the central base plate 112 a shaft hole 112a, through which one end of the rotating shaft 300 passes, and a counter-pressure chamber 112b for pressing the orbital spiral 400 towards the stationary spiral 500 can be formed. Here, at one end of the rotating shaft 300, an eccentric bushing 310 is formed for converting the rotational motion of the rotating shaft 300 into the orbital motion of the orbital spiral 400, and the counter-pressure chamber 112b provides space for the rotation of the eccentric bushing 310.

[0037] Furthermore, an intake flow path (not shown) can be formed on the outer circumference of the central base plate 112, which directs the refrigerant flowing into the motor intake chamber S1 to the spiral intake chamber S2, as will be described later.

[0038] The front housing 120 can have a front base plate 122, which points towards the central base plate 112 and supports the other end of the rotating shaft 300, and a front side plate 124, which projects from an outer circumference of the front base plate 122, coupled to the central side plate 114 and supports the motor 200.

[0039] Here, the central base plate 112, the central side plate 114, the front base plate 122 and the front side plate 124 can form the motor mounting space S1.

[0040] Furthermore, an intake opening (not shown) can be formed on the front side plate 124, which directs a refrigerant having an intake pressure from outside the engine mounting chamber S1.

[0041] As in the Fig. As shown in Figures 2, 3 and 5 to 8, the rear housing 130 can have a discharge chamber D for receiving the refrigerant discharged from the compression chamber C, a discharge opening 131 that directs the refrigerant from the discharge chamber D to outside the housing 100, an inlet opening 133 into which medium-pressure refrigerant is introduced from outside the housing 100, and an inlet chamber I that receives the refrigerant introduced through the inlet opening 133, wherein at least a part of the inlet chamber I can be formed to be received in the discharge chamber D, wherein at least a part of the discharge opening 131 can be formed to be received in the inlet chamber I, and wherein at least a part of the inlet opening 133 can be formed to be received in the discharge chamber D.

[0042] In particular, the rear housing 130 can have a rear base plate 132 opposite the central base plate 112, a first annular wall 134 projecting from the rear base plate 132 and located at the outermost side in the radial direction of the rear housing 130, a second annular wall 136 projecting from the rear base plate 132 and incorporated in the first annular wall 134, and a third annular wall 138 projecting from the rear base plate 132 and incorporated in the second annular wall 136, wherein the first annular wall 134, the second annular wall 136 and the third annular wall 138 can be formed to have different heights.

[0043] The first annular wall 134 can be formed in an annular shape having a diameter approximately equal to the outer circumference of the central base plate 112, can be coupled to the outer circumference of the central base plate 112 and can form the spiral receiving space S2.

[0044] The second annular wall 136 can be formed in an annular shape which has a smaller diameter than the first annular wall 134, can be in contact with the outer circumference of a fixed base plate 510 to be described later and can form the ejection chamber D.

[0045] Here, the second annular wall 136 is formed to be in contact with a fixed base plate 521 to be described later when the rear housing 130 is coupled to the central housing 110, whereby the fastening force between the central housing 110 and the fixed spiral 500 can be improved by pressing the fixed spiral 500 towards the central housing 110, so that leakage between the fixed spiral 500 and the central housing 110 can be prevented.

[0046] The third annular wall 138 can be formed in an annular shape having a smaller diameter than the second annular wall 136, can be spaced apart from a fixed base plate 510 to be described later, and can be covered by a cover plate 710 to be described later, to form the inlet chamber I.

[0047] The third annular wall 138 can have a fastening groove 138a, into which a fastening bolt 770 is inserted, which fastens the injection valve assembly 700 to the third annular wall 138, and a first positioning groove 138b, into which a positioning pin 780 is inserted, which aligns a cover plate 710, an injection valve 720 and a valve plate 730, which are to be described later, into a predetermined position.

[0048] The ejection opening 131 is formed in the rear base plate 132, and the ejection opening 131 can be formed to extend from a center of the rear base plate 132 to a side of an outer circumference of the rear base plate 132 in a radial direction of the rear base plate 132.

[0049] Furthermore, an exhaust opening inlet 131a can be formed in the rear base plate 132, which directs the refrigerant from the exhaust chamber D to the exhaust opening 131.

[0050] On the other hand, a tubular oil separator (not shown) is provided inside the discharge opening 131, which separates the oil and refrigerant, and the oil separator (not shown) can be designed such that the refrigerant is separated from the oil during the discharge process, in which the refrigerant introduced into the discharge opening inlet 131a flows along an intermediate space between an outer circumferential surface of the oil separator (not shown) and an inner circumferential surface of the discharge opening 131 to the central side of the rear base plate 132 and is then reversed and discharged along an inner circumferential surface of the oil separator (not shown) to a side of the outer circumference of the rear base plate 132.

[0051] Furthermore, the inlet opening 133 is formed in the rear base plate 132; the inlet opening can be formed such that it extends from the other side of the outer circumference of the rear base plate 132 to the center of the rear base plate 132 in the radial direction of the rear base plate 132, and can communicate with the inlet chamber I.

[0052] Since the third annular wall 138 is formed to be received within the second annular wall 136, and the third annular wall 138 is spaced apart from the fixed base plate 510 (to be described later) and covered by the injection valve assembly 700, at least part of the inlet chamber I can be received within the outlet chamber D. That is, one side of the inlet chamber I can be formed such that the outlet chamber D overlaps the third annular wall 138 arranged between them in the radial direction of the rear housing 130, and one end of the inlet chamber I can be formed such that the outlet chamber D overlaps the injection valve assembly 700 arranged between them in the axial direction of the rear housing 130.

[0053] Since the ejection opening 131 extends from the center of the rear base plate 132 to one side of the outer circumference of the rear base plate 132 in the radial direction of the rear base plate 132, at least part of the ejection opening 131 can be accommodated in the inlet chamber I. That is, at least part of the ejection opening 131 can be formed such that the inlet chamber I overlaps with a wall section of the interposed ejection opening 131 in the axial direction of the rear housing 130.

[0054] Since the inlet opening 133 extends from the other side of the outer circumference of the rear base plate 132 to the center of the rear base plate 132 in the radial direction of the rear base plate 132, at least part of the inlet opening 133 can be accommodated in the ejection chamber D. That is, at least part of the inlet opening 133 can be formed such that the ejection chamber D overlaps with a wall section of the inlet opening 133 arranged between them in the axial direction of the rear housing 130.

[0055] On the other hand, the discharge port 131 and the inlet port 133 can be configured such that the refrigerant from the discharge port 131 and the refrigerant from the inlet port 133 flow towards each other in a cross-flow direction. That is, an angle can be formed between an outlet of the discharge port 131 and an inlet of the inlet port 133 with respect to the center of the rear casing 130, which is greater than or equal to 0 degrees and less than 90 degrees.

[0056] As in Fig. As shown in Figure 2, the motor 200 can comprise a stator 210 attached to the front side plate 124 and a rotor 220 which is rotated inside the stator 210 by interaction with the stator 210.

[0057] As in Fig. As shown in Figure 2, the rotating shaft 300 is coupled to the rotor 220 and passes through a center of the rotor 220, and one end of the rotating shaft 300 passes through the shaft hole 112a of the central base plate 112 and the other end of the rotating shaft 300 can be supported by the front base plate 122.

[0058] As in the Fig. As shown in Figures 2 and 16 to 19, the orbital spiral 400 can be arranged between the central base plate 112 and the stationary spiral 500 and has a disc-shaped circumferential base plate 410, a circumferential sheath 420 projecting from a center of the circumferential base plate 410 towards the stationary spiral 500, and a knob section 430 projecting from the center of the circumferential base plate 410 to the opposite side of the circumferential sheath 420 and coupled to the eccentric bushing 310.

[0059] As in the Fig. As shown in Figures 2 to 4, 8, 13 to 19, the stationary spiral 500 can comprise a disk-shaped stationary base plate 510, a stationary sheathing 520 projecting from a center of the stationary base plate 510 and engaging in the circumferential sheathing 420, and a stationary side plate 530 projecting from an outer circumference of the stationary base plate 510 and coupled to the central base plate 112.

[0060] The stationary base plate 510 can include an ejection hole 512, which ejects the refrigerant from the compression chamber C into the ejection chamber D, and an injection hole 514, which directs the refrigerant ejected from the injection valve assembly 700 to the compression chamber C.

[0061] The discharge hole 512 can be formed in a plurality to prevent the refrigerant from being over-compressed, and the plurality of discharge holes 512 can be opened and closed by a discharge valve 600 arranged between the stationary base plate 510 and the injection valve assembly 700.

[0062] In particular, the compression chamber C comprises a first compression chamber C1, which is positioned on the distal side in the radial direction of the spiral receiving space S2 and has a first pressure, a second compression chamber C2, which is located on the centripetal side in the radial direction of the spiral receiving space S2 with respect to the first compression chamber C1 and has a second pressure which is higher than the first pressure, and a third compression chamber C3, which is located on the centripetal side in the radial direction of the spiral receiving space S2 with respect to the second compression chamber C2 and has a third pressure which is higher than the second pressure, wherein the first compression chamber C1, the second compression chamber C2 and the third compression chamber C3 can each be formed as a pair.

[0063] That is, the first compression chamber C1 can comprise a first outer compression chamber C11, formed by an outer circumferential surface of the circumferential casing 420 and an inner circumferential surface of the fixed casing 520, and a first inner compression chamber C12, formed by an inner circumferential surface of the circumferential casing 420 and an outer circumferential surface of the fixed casing 520.

[0064] The second compression chamber C2 can comprise a second outer compression chamber C21, formed by the outer circumferential surface of the circumferential casing 420 and the inner circumferential surface of the fixed casing 520, and a second inner compression chamber C22, formed by the inner circumferential surface of the circumferential casing 420 and the outer circumferential surface of the fixed casing 520.

[0065] The third compression chamber C3 can comprise a third outer compression chamber C31, formed by the outer circumferential surface of the circumferential casing 420 and the inner circumferential surface of the fixed casing 520, and a third inner compression chamber C32, formed by the inner circumferential surface of the circumferential casing 420 and the outer circumferential surface of the fixed casing 520.

[0066] In this case, the discharge port 512 can have a main discharge port 512a, formed in the center of the fixed base plate 510 to discharge the refrigerant from the third outer compression chamber C31 and the third inner compression chamber C32; a first secondary discharge port 512b, formed outside the fixed base plate 510 in a radial direction with respect to the main discharge port 512a to discharge the refrigerant from the second outer compression chamber C21; and a second secondary discharge port 512c, formed outside the fixed base plate 510 in a radial direction with respect to the main discharge port 512a and on the opposite side of the first secondary discharge port 512b with respect to the main discharge port 512a to discharge the refrigerant from the second inner compression chamber C22.

[0067] Furthermore, the discharge valve 600 can have an opening / closing main section 610 that opens and closes the main discharge port 512a, a first opening / closing subsection 630 that opens and closes the first secondary discharge port 512b, a second opening / closing subsection 650 that opens and closes the second secondary discharge port 512c, a mounting section 670 that is attached to the fixed base plate 510, a support main section 620 that extends from the opening / closing main section 610 to the mounting section 670, a first support subsection 640 that extends from the first opening / closing subsection 630 to the mounting section 670, and a second support subsection 660 that extends from the second opening / closing subsection to the mounting section 670.

[0068] Here, the main opening / closing section 610 opens the main discharge port 512a when the pressures of the third outer compression chamber C31 and the third inner compression chamber C32 reach the discharge pressure level; the first opening / closing subsection 630 opens the first auxiliary discharge port 512b when the pressure of the second outer compression chamber C21 exceeds the second pressure, thus reducing the pressure of the second outer compression chamber C21 to the second pressure; the second opening / closing subsection 650 opens the second auxiliary discharge port 512c when the pressure of the second inner compression chamber C22 exceeds the second pressure, thus reducing the pressure of the second inner compression chamber C22 to the second pressure, thereby preventing the pressure of the refrigerant discharged from the main discharge port 512a from being excessively higher than the discharge pressure. That is, over-compression can be prevented.

[0069] To prevent a pressure imbalance between the second outer compression chamber C21 and the second inner compression chamber C22, the first auxiliary ejection port 512b and the second auxiliary ejection port 512c can be temporarily formed to communicate simultaneously with the second outer compression chamber C21 and the second inner compression chamber C22. That is, once communication begins between the first auxiliary ejection port 512b and the second outer compression chamber C21, communication can begin between the second auxiliary ejection port 512c and the second inner compression chamber C22.

[0070] Furthermore, the first secondary ejection port 512b and the second secondary ejection port 512c can preferably be configured to be simultaneously blocked by the second outer compression chamber C21 and the second inner compression chamber C22. That is, if the communication between the first secondary ejection port 512b and the second outer compression chamber C21 is terminated, the communication between the second secondary ejection port 512c and the second inner compression chamber C22 can also be terminated.

[0071] To minimize the increase in cost and weight caused by the ejection valve 600, the opening / closing main section 610, the first opening / closing subsection 630, the second opening / closing subsection 650 and the mounting section 670, the support main section 620, the first support subsection 640 and the second support subsection 660 can be formed integrally, and the circumferential width of the mounting section 670 can be formed which is smaller than a distance between the first opening / closing subsection 630 and the second opening / closing subsection 650, and the ejection valve 600 can be attached to the fixed base plate 510 by a mounting element 680.Here, the single fastening element 680 can preferably be attached to an inlet 532 of a fixed casing, which has a relatively large thickness and height, which will be described later, so that the discharge valve 600 receives sufficient support even when it is attached to the fixed base plate 510 by the single fastening element 680.

[0072] Furthermore, the discharge valve 600 is not only integrally formed, as described above, but also has a narrow width of the mounting section 670 and is attached to the fixed base plate 510 by the single mounting element 680, so that the degree of freedom in the design is low, and at least one of the first support subsection 640 and the second support subsection 660 can obstruct the injection hole 514; to prevent this, at least one of the first support subsection 640 and the second support subsection 660 can include a bypass section 690 which is formed to be engraved in the direction of the main support section 620.

[0073] The injection hole 514 can be formed as a long hole to increase the flow velocity of the refrigerant injected into the compression chamber C.

[0074] Furthermore, the injection hole 514 can have a uniform cross-sectional shape, so that no pressure loss and no loss of flow velocity occur while the refrigerant passes through the injection hole 514. This means that the inner diameter of the injection hole 514 can be formed to have a predetermined value, regardless of its axial position.

[0075] Furthermore, the injection port 514 can be formed in a plurality to supply the refrigerant discharged from the injection valve assembly 700 to the pair of first compression chambers C1. That is, the injection port 514 can comprise a first injection port 514a, which can communicate with the first outer compression chamber C11, and a second injection port 514b, which can communicate with the first inner compression chamber C12, wherein the first injection port 514a and the second injection port 514b can be formed on opposite sides with respect to an imaginary line connecting the first secondary discharge port 512b and the second secondary discharge port 512c.

[0076] To prevent a pressure imbalance between the first outer compression chamber C11 and the first inner compression chamber C12, the injection port 514 can be formed here to communicate with both the first outer compression chamber C11 and the first inner compression chamber C12 simultaneously. That is, when communication begins between the first injection port 514a and the first outer compression chamber C11, communication can begin between the second injection port 514b and the first inner compression chamber C12, as shown in the Fig. 16, Fig. 17, Fig. 18, Fig. 19 to Fig. 20 shown.

[0077] The injection port 514 can preferably be configured to be blocked simultaneously with the first outer compression chamber C11 and the first inner compression chamber C12. That is, when the communication between the first injection port 514a and the first outer compression chamber C11 is terminated, the communication between the second injection port 514b and the first inner compression chamber C12 can be terminated, as shown in the Fig. 16, Fig. 17, Fig. 18, Fig. 19 to Fig. 20 shown.

[0078] Meanwhile, the stationary base plate 510 can further include an insertion groove 516 for a small-diameter section to prevent refrigerant leakage when the refrigerant flows from the injection valve assembly 700 to the first injection port 514a and the second injection port 514b. That is, the stationary base plate 510 can further include a first insertion groove 516a for a small-diameter section, into which a first small-diameter section 732ab, to be described later, is inserted, and a second insertion groove 516b for a small-diameter section, into which a second small-diameter section 732bb, to be described later, is inserted.

[0079] In particular, the stationary base plate 510 can comprise an upper surface 510a of the stationary base plate opposite the injection valve assembly 700 and a lower surface 510b of the stationary base plate, which forms the rear surface of the upper surface 510a of the stationary base plate and is opposite the rotating spiral 400.

[0080] Furthermore, the first insertion groove 516a for a small diameter section is impressed from the upper surface 510a of the fixed base plate towards the lower surface 510b of the fixed base plate, and a first small diameter section 732ab, to be described later, is inserted therein, and the first injection hole 514a is impressed from the lower surface 510b of the fixed base plate towards the upper surface 510a of the fixed base plate and can communicate with the first insertion groove 516a for a small diameter section.

[0081] Furthermore, the second insertion groove 516b for a small diameter section is impressed from the upper surface 510a of the fixed base plate towards the lower surface 510b of the fixed base plate, and a second small diameter section 732bb, to be described later, is inserted therein, and the second injection hole 514b is impressed from the lower surface 510b of the fixed base plate towards the upper surface 510a of the fixed base plate and can communicate with the second insertion groove 516b for a small diameter section.

[0082] As in Fig. As shown in Figure 4, an inner diameter of the first small-diameter section 732ab (inner diameter of a first outlet 736a to be described later) can be formed here to be greater than or equal to an inner diameter of the first injection hole 514a, and the inner diameter of the first insertion groove 516a for a small-diameter section can be formed at the same level as an outer diameter of the first small-diameter section 732ab to be described later, so that a first small-diameter section 732ab to be described later can be inserted into the first insertion groove 516a for the small-diameter section 516a and no pressure loss and no flow velocity loss occurs while the refrigerant flows from the injection valve assembly 700 to the first injection hole 514a.This means that since the outer diameter of the first small-diameter section 732ab to be described later is larger than the inner diameter of the first small-diameter section 732ab to be described later, the inner diameter of the first insertion groove 516a for a small-diameter section can be larger than the inner diameter of the first injection hole 514a.

[0083] Furthermore, an inner diameter of the second small-diameter section 732bb (inner diameter of a second outlet 736b to be described later) can be formed to be greater than or equal to the inner diameter of the second injection hole 514b, and the inner diameter of the second insertion groove 516b for a small-diameter section can be formed at the same level as an outer diameter of the second small-diameter section 732bb to be described later, so that a second small-diameter section 732bb to be described later can be inserted into the second insertion groove 516b for a small-diameter section and no pressure loss and no flow velocity loss occurs while the refrigerant flows from the injection valve assembly 700 to the second injection hole 514b.This means that the inner diameter of the second insertion groove 516b for a small diameter section can be formed to be larger than the inner diameter of the second injection hole 514b, since an outer diameter of the second small diameter section 732bb to be described later is larger than an inner diameter of the second small diameter section 732bb to be described later.

[0084] The fixed casing 520 can be formed, for example, to extend in a logarithmic spiral from the central side of the fixed spiral 500 to the outer circumferential side of the fixed spiral 500.

[0085] The fixed side plate 530 is formed in a ring-shaped form extending along the outer circumference of the fixed base plate 510 and can include an inlet 532 of the fixed casing which is connected to the fixed casing 520 on one side.

[0086] In the inlet 532 of the fixed casing, an axial height of the inlet 532 of the fixed casing can be formed at the same level as an axial height of the fixed casing 520, so that the refrigerant of the compression chamber C does not escape from the inlet 532 of the fixed casing.

[0087] Furthermore, a radial thickness of the inlet 532 of the fixed casing can be formed in order to be thicker than a radial thickness of the fixed casing 520, so that the support stiffness of the fixed casing 520 is improved.

[0088] To reduce the weight and cost of the fixed spiral 500, the fixed side plate 530 can be formed such that a radial section thickness, with the exception of the inlet 532 of the fixed casing, is thinner than a radial thickness of the inlet 532 of the fixed casing.

[0089] The injector assembly 700 can be formed on an end surface of the third annular wall 138 to communicate and block between the inlet chamber I and the injection hole 514.

[0090] In particular, the injection valve assembly 700, as described in the Fig. Figures 2 to 4 and 8 to 12 show a cover plate 710 attached to the end surface of the third annular wall 138 to cover the inlet chamber I, a valve plate 730 attached to the cover plate 710 from the opposite side of the inlet chamber I with respect to the cover plate 710, and an injection valve 720 arranged between the cover plate 710 and the valve plate 730.

[0091] The cover plate 710 can comprise an upper cover plate surface 710a opposite the inlet chamber I and the third annular wall 138, a lower cover plate surface 710b opposite the valve plate 730 and the injection valve 720, and an injection valve sealing groove 710c formed concavely from the lower cover plate surface 710b to the center of the cover plate 710.

[0092] The cover plate 710 can further include an inlet 712 for communication between the inlet chamber I and a chamfered space 734 to be described later, a second mounting hole 714 which communicates with the mounting groove 138a and is penetrated by the mounting bolt 770, and a first positioning hole 716 which communicates with the first positioning groove 138b and is penetrated by the positioning pin 780.

[0093] The inlet 712 can be formed in the middle of the cover plate 710 and can be formed by the cover plate 710 from the upper cover plate surface 710a to the injector sealing groove 710c.

[0094] The second fixing hole 714 can be formed on an outer circumference of the cover plate 710 and can be formed through the cover plate 710 from the upper cover plate surface 710a to the lower cover plate surface 710b.

[0095] The first positioning hole 716 is formed between the inlet 712 and the second mounting hole 714 in the radial direction of the cover plate 710 and can be formed by the cover plate 710 from the upper cover plate surface 710a to the injection valve sealing groove 710c.

[0096] The injector 720 can comprise a head 722 that opens and closes the inlet 712, a leg 724 that supports the head 722, and a periphery 726 that supports the leg 724.

[0097] The head 722 can be formed in a disc-shaped form, having an outer diameter that is larger than the inner diameter of the inlet 712.

[0098] The leg 724 can be formed in a plate shape, extending from the head 722 to one side of the periphery 726 in one direction.

[0099] The circumference 726 can be formed in a ring-shaped form that accommodates the head 722 and the leg 724, while they are received in the injector sealing groove 710c.

[0100] Furthermore, the periphery 726 can include a second positioning hole 726a, which communicates with the first positioning hole 716 and is penetrated by the positioning pin 780.

[0101] Here, the axial thickness of the periphery 726 in the injector 720 can be formed to be greater than or equal to the axial depth of the injector sealing groove 710c (more precisely, the distance between a base surface of the injector sealing groove 710c and an upper valve plate surface 730a to be described later), so that the periphery 726 is fixed without a separate fastening element for fixing the injector 720 by being pressed between the injector sealing groove 710c and the valve plate 730. To prevent the possibility that the periphery 726 is not compressed between the injector sealing groove 710c and the valve plate 730 due to tolerances, it may be preferable at this point for the axial thickness of the periphery 726 to be designed to be greater than the axial depth of the injector sealing groove 710c.

[0102] The valve plate 730 can comprise an upper valve plate surface 730a opposite the cover plate 710 and the injector 720 and a lower valve plate surface 730b opposite the fixed spiral 500, while forming a rear surface of the upper valve plate surface 730a.

[0103] Furthermore, the valve plate 730 can include a projection 732 extending from the lower valve plate surface 730b towards the first injection hole 514a and the second injection hole 514b. That is, the valve plate 730 can include a first projection 732a extending from one side of the lower valve plate surface 730b towards the first injection hole 514a, and a second projection 732b extending from the other side of the lower valve plate surface 730b towards the second injection hole 514b.

[0104] Furthermore, the valve plate 730 can have a sloping space 734, which serves as a holder for the injection valve 720 and receives the refrigerant flowing through the inlet 712, a first outlet 736a, which is formed in the first projection 732a and communicates with the first injection hole 514a, a second outlet 736b, which is formed in the second projection 732b and communicates with the second injection hole 514b, a first connecting flow path 738a, which directs the refrigerant from the sloping space 734 to the first outlet 736a, and a second connecting flow path 738b, which directs the refrigerant from the sloping space 734 to the second outlet 736b.

[0105] The upper valve plate surface 730a can be formed as a plane that is in contact with the lower cover plate surface 710b and the periphery 726 of the injection valve 720.

[0106] The chamfered space 734 can be formed to be imprinted from the upper valve plate surface 730a.

[0107] The chamfered space 734 can include a mounting surface that supports the head 722 and leg 724 of the injector 720 when the injector 720 opens the inlet 712.

[0108] The first outlet 736a may be imprinted from the end surface of the first projection 732a (more precisely, an end surface of a first section with a small diameter 732ab to be described later).

[0109] The second outlet 736b may be imprinted from the end surface of the second projection 732b (more precisely, an end surface of a second section with a small diameter 732ab to be described later).

[0110] The first connecting flow path 738a can be imprinted from the upper valve plate surface 730a and can be formed for communication between one side of the chamfered space 734 and the first outlet 736a.

[0111] The second connecting flow path 738b can be imprinted from the upper valve plate surface 730a and can be formed for communication between the other side of the beveled space 734 and the second outlet 736b.

[0112] The lower valve plate surface 730b can be formed to be spaced apart from the upper surface 510a of the fixed base plate, so that the discharge valve 600 can be arranged between the upper surface 510a of the fixed base plate and the lower valve plate surface 730b, and the refrigerant discharged from the discharge hole 512 can flow into the discharge chamber D.

[0113] The first projection 732a can comprise a first large-diameter section 732aa extending from one side of the lower valve plate surface 730b towards the first injection hole 514a, and a first small-diameter section 732ab extending from the first large-diameter section 732aa towards the first injection hole 514a.

[0114] In the first large-diameter section 732aa, the outer diameter of the first large-diameter section 732aa can be larger than the inner diameter of the first insertion groove 516a for a small-diameter section, so that the first large-diameter section 732aa cannot be inserted into the first insertion groove 516a for a small-diameter section, and a third sealing element 760, to be described later, can be compressed between an end surface of the first large-diameter section 732aa and the upper surface 510a of the fixed base plate.

[0115] In the first small-diameter section 732ab, the outer diameter of the first small-diameter section 732ab can be smaller than the outer diameter of the first large-diameter section 732aa and can be formed at the same level as the inner diameter of the first insertion groove 516a for a small-diameter section, so that the first small-diameter section 732ab can be inserted into the first insertion groove 516a for a small-diameter section.

[0116] In the first small-diameter section 732ab, a projection length of the first small-diameter section 732ab (the axial distance between the end surface of the first large-diameter section 732aa and an end surface of the first small-diameter section 732ab) can be greater than the pre-deformation thickness of a third sealing element 760 to be described later, and can be less than or equal to the sum of the pre-deformation thickness of a third sealing element 760 to be described later and the axial depth of the first insertion groove 516a for a small-diameter section, such that the end surface of the first small-diameter section 732ab cannot be in contact with the base surface of the first insertion groove 516a for a small-diameter section.and a gap between the end surface of the first large-diameter section 732aa and the upper surface 510a of the fixed base plate can be less than or equal to the thickness of the deformation (thickness before compression between the upper surface 510a of the fixed base plate and the end surface of the first large-diameter section 732aa) of a third sealing element 760 to be described later, such that a third sealing element 760 to be described later can be compressed between the end surface of the first large-diameter section 732aa and the upper surface 510a of the fixed base plate. It may be desirable here only in the case that the third sealing element 760, to be described later, is not compressed between the end surface of the first large-diameter section 732aa and the upper surface 510a of the fixed base plate due to tolerance.the projection length of the first small-diameter section 732ab is designed such that it is greater than the thickness before deformation of a third sealing element 760 to be described later and less than the sum of the thickness before deformation of a third sealing element 760 to be described later and the axial depth of the first insertion groove 516a for a small-diameter section.

[0117] The second lead 732b can be formed similarly to the first lead 732a.

[0118] That is, the second projection 732b can include a second large-diameter section 732ba projecting from the other side of the lower valve plate surface 730b towards the second injection hole 514b, and a second small-diameter section 732bb projecting from the second large-diameter section 732ba towards the second injection hole 514b.

[0119] In the second large-diameter section 732ba, an outer diameter of the second large-diameter section 732ba can be larger than an inner diameter of the second insertion groove 516b for a small-diameter section, so that the second large-diameter section 732ba cannot be inserted into the second insertion groove 516b for a small-diameter section, and a third sealing element 760, to be described later, can be compressed between an end surface of the second large-diameter section 732ba and the upper surface 510a of the fixed base plate.

[0120] In the second small-diameter section 732bb, the outer diameter of the second small-diameter section 732bb can be smaller than the outer diameter of the second large-diameter section 732ba and be formed at the same level as the inner diameter of the second insertion groove 516b for a small-diameter section, so that the second small-diameter section 732bb can be inserted into the second insertion groove 516b for a small-diameter section.

[0121] In the second small-diameter section 732bb, a projection length of the second small-diameter section 732bb (the axial distance between the end surface of the second large-diameter section 732ba and an end surface of the second small-diameter section 732bb) can be greater than the pre-deformation thickness of a third sealing element 760 to be described later, and can be formed to be less than or equal to the sum of the pre-deformation thickness of a third sealing element 760 to be described later and the axial depth of the second insertion groove 516b for a small-diameter section, such that the end surface of the second small-diameter section 732bb cannot be in contact with the base surface of the second insertion groove 16b for a small-diameter section.and a gap between the end surface of the second large-diameter section 732ba and the upper surface 510a of the fixed base plate can be less than or equal to the thickness of the deformation (thickness before compression between the upper surface 510a of the fixed base plate and the end surface of the second large-diameter section 732ba) of a third sealing element 760 to be described later, such that a third sealing element 760 to be described later can be compressed between the end surface of the second large-diameter section 732ba and the upper surface 510a of the fixed base plate. It may only be desirable here if the third sealing element 760, to be described later, is not compressed between the end surface of the second large-diameter section 732ba and the upper surface 510a of the fixed base plate due to tolerance.the projection length of the second small-diameter section 732bb is designed such that it is greater than the thickness before deformation of a third sealing element 760 to be described later and less than the sum of the thickness before deformation of a third sealing element 760 to be described later and the axial depth of the second insertion groove 516b for a small-diameter section 516a.

[0122] The valve plate 730 can further include a first mounting hole 739a formed by the valve plate 730 from the upper valve plate surface 730a to the lower valve plate surface 730b in the outer circumference of the valve plate 730 to communicate with the second mounting hole 714 and to be penetrated by the mounting bolt 770.

[0123] In addition, the valve plate 730 can further include a second positioning groove 739b, which is embossed from the upper valve plate surface 730a, to communicate with the second positioning hole 726a, and so that the positioning pin 780 is inserted therein.

[0124] Here, the injector assembly 700 can be aligned by the positioning pin 780, the first positioning hole 716, the second positioning hole 726a, the first positioning groove 138b, and the second positioning groove 739b, and then fastened to the rear housing 130 by the mounting bolt 770, the first mounting hole 739a, the second mounting hole 714, and the mounting groove 138a. That is, one end of the positioning pin 780 passes through the first positioning hole 716 and is inserted into the first positioning groove 138b, and the other end of the positioning pin 780 passes through the second positioning hole 726a and is inserted into the second positioning groove 739b, so that the cover plate 710, the injector 720, and the valve plate 730 can be positioned at predetermined locations.The fastening bolt 770 then passes through the first fastening hole 739a and the second fastening hole 714 and is attached to the fastening groove 138a, so that the injection valve assembly 700 can be attached to the rear housing 130.

[0125] In the meantime, as in the Fig. Figures 2 to 4 and 8 show that when the injection valve assembly 700 is coupled to the rear housing 130, a first sealing element 740 is arranged between the upper cover plate surface 710a and the third annular wall 138, and a second sealing element 750 is arranged between the upper valve plate surface 730a and the lower cover plate surface 710b.

[0126] As in the Fig. As shown in Figures 2 to 4 and 12, when the injection valve assembly 700 is attached to the stationary spiral 500, a third sealing element 760 can be arranged between the end surfaces of the large diameter sections 732aa, 732ba and the upper surface 510a of the stationary base plate.

[0127] Here, in the third sealing element 760, as described above, the thickness before deformation of the third sealing element 760 can be greater than or equal to the gap between the end surfaces of the large diameter sections 732aa, 732ba and the upper surface 510a of the fixed base plate, so that the third sealing element 760 can be compressed between the end surfaces of the large diameter sections 732aa, 732ba and the upper surface 510a of the fixed base plate.

[0128] For the time being, the unspecified reference numbers 718 and 719 denote a first groove 718 and a second groove 719 formed in the cover plate 710, and the unspecified reference numbers 518 and 519 denote a third groove 518 and a fourth groove 519 formed in the fixed base plate 510.

[0129] The first groove 718 serves to reduce the contact area between the head 722 of the injector 720 and the cover plate 710 in order to reduce impact noise between the head 722 of the injector 720 and the cover plate 710, and to prevent foreign matter from becoming trapped between the head 722 of the injector 720 and the cover plate 710b by collecting and expelling foreign matter. It can be formed in an annular shape that surrounds the periphery of the inlet 712 while being impressed by the injector sealing groove 710c, as shown in Fig. Figure 10 illustrates this. An inner circumference of the first groove 718 can be formed to overlap with an outer circumference of the head 722 of the injector 720 in the axial direction, and an outer circumference of the first groove 718 can be formed not to overlap with the head 722 of the injector 720 in the axial direction. That is, an inner diameter of the first groove 718 can be smaller than an outer diameter of the head 722 of the injector 720, and an outer diameter of the first groove 718 can be larger than an outer diameter of the head 722 of the injector 720. The reason for the outer diameter of the first groove 718 being larger than the outer diameter of the head 722 of the injector 720 is to allow foreign matter collected in the first groove 718 to be ejected into the chamfered space 734.

[0130] The second groove 719 serves to collect and expel foreign matter to prevent foreign matter from becoming trapped between the leg 724 of the injector 720 and the cover plate 710, and can be formed to be impressed by the injector sealing groove 710c into a position opposite the leg 724 of the injector 720, as shown in Fig. Figure 10 shows. Furthermore, the second groove 719 is formed in the form of a long hole, a center of the second groove 719 is formed to overlap with the leg 724 of the injector 720 in the axial direction, and both ends of the second groove 719 can be formed to not overlap with the leg 724 of the injector 720 in the axial direction. This means that the longitudinal axis direction of the second groove 719 and the width direction of the leg 724 of the injector 720 can be parallel to each other, and the longitudinal axis direction of the second groove 719 can be formed to be greater than the width of the leg 724 of the injector 720. Here, the longitudinal axis length of the second groove 719 is formed to be greater than the width of the leg 724 of the injector 720, in order to allow foreign matter collected in the second groove 219 to be ejected into the chamfered space 734.

[0131] Similar to the first groove 718, the third groove 518 serves to reduce the contact area between the opening / closing main section 610 of the ejection valve 600 and the stationary base plate 510 in order to reduce impact noise between the opening / closing main section 610 of the ejection valve 600 and the stationary base plate 510, and to prevent foreign matter from becoming trapped between the opening / closing main section 610 of the ejection valve 600 and the stationary base plate 510 by collecting and ejecting it. It can be formed in an annular shape that surrounds the main ejection hole 512a while being impressed by the upper surface 510a of the stationary base plate, as shown in the Fig. 8 and Fig. Figure 13 shows that an inner circumference of the third groove 518 can be formed to overlap with an outer circumference of the opening / closing section 610 of the ejection valve 600 in the axial direction, and an outer circumference of the third groove 518 can be formed not to overlap with the opening / closing section 610 of the ejection valve 600 in the axial direction. This means that the inner diameter of the third groove 518 can be smaller than the outer diameter of the opening / closing section 610 of the discharge valve 600, and the outer diameter of the third groove 518 can be larger than the outer diameter of the opening / closing section 610 of the discharge valve 600. The reason the outer diameter of the third groove 518 is larger than the outer diameter of the opening / closing section 610 of the discharge valve 600 is to allow foreign matter collected in the third groove 518 to be discharged into the discharge chamber D.

[0132] Similar to the second groove 719, the fourth groove 519 serves to collect and expel foreign matter to prevent foreign matter from becoming trapped between the main support section 620, the first support subsection 640, and the second support subsection 660 (hereinafter referred to as the support sections) of the discharge valve 600 and the fixed base plate 510, and may be formed to be impressed by the upper surface 510a of the fixed base plate at a position opposite the support section of the discharge valve 600, as shown in the Fig. 8 and Fig. Figure 13 illustrates this. Furthermore, the fourth groove 519 is formed in the form of an elongated hole. A central section of the fourth groove 519 is designed to overlap the support section of the discharge valve 600 in an axial direction, while both ends of the fourth groove 519 may be designed not to overlap the support section of the discharge valve 600 in an axial direction. That is, the longitudinal axis of the fourth groove 519 and the width of the support section of the discharge valve 600 may be parallel to each other, and the longitudinal axis of the fourth groove 519 may be greater than the width of the support section of the discharge valve 600. Here, the longitudinal axis length of the fourth groove 519 is designed to be greater than the width of the support section of the discharge valve 600 to allow foreign matter collected in the fourth groove 519 to be discharged into the discharge chamber D.

[0133] The effects of the scroll compressor according to the embodiment of the invention are described below.

[0134] This means that the rotating shaft 300 can rotate together with the rotor 220 when current is applied to the motor 200.

[0135] The spiral 400 can be moved in a circular motion by absorbing the rotational force from the rotating shaft 300 through the eccentric bushing 310.

[0136] Accordingly, the volume of the compression chamber C can be reduced while a continuous movement towards the central side takes place.

[0137] Furthermore, the refrigerant, which has an intake pressure, can be introduced into the compression chamber C through the intake opening (not shown), the engine intake chamber S1, the intake flow path (not shown) and the spiral intake chamber S2.

[0138] Furthermore, the refrigerant drawn into the compression chamber C can be compressed as it moves along a path of movement in the compression chamber C towards the center and is expelled through the discharge hole 512 into the discharge chamber D.

[0139] Furthermore, the discharge pressure refrigerant ejected into discharge chamber D can be ejected outside the compressor through discharge opening 131.

[0140] In this embodiment, the scroll compressor includes the injection flow path (inlet opening 133, inlet chamber I, injection valve assembly 700, injection hole 514) for directing the medium-pressure refrigerant to the compression chamber C, compresses the intake-pressure refrigerant and the medium-pressure refrigerant, and expels them. This allows the quantity of expelled refrigerant to be increased, unlike when only the intake-pressure refrigerant is drawn in, compressed, and expelled. This improves the performance and efficiency of the compressor.

[0141] Since, because there is no separate housing, the rear housing 130 has the ejection chamber D and the ejection opening 131 as well as the inlet opening 133 and the inlet chamber I, that is to say, the rear housing 130, which has the ejection chamber D, the ejection opening 131, the inlet opening 133 and the inlet chamber I, is formed integrally, the possibility of leakage is reduced and size, cost and weight can be reduced.

[0142] Since at least part of the inlet chamber I is contained within the discharge chamber D—that is, the side of the inlet chamber I overlaps with the discharge chamber D, and the third annular wall 138 is positioned between them—and the end of the inlet chamber I overlaps with the discharge chamber D, and the injection valve assembly 700 is positioned between them, the refrigerant directed into the injection port 514 can exchange heat with the refrigerant in the discharge chamber D through the third annular wall 138 and the injection valve assembly 700. This means that the refrigerant in the inlet chamber I and the refrigerant passing through the injection valve assembly 700 can be heated by absorbing heat from the refrigerant in the discharge chamber D. Accordingly, it is possible to prevent a liquid refrigerant from being injected into the compression chamber C through the injection port 514.

[0143] Since at least part of the discharge opening 131 is incorporated into the inlet chamber I, that is, at least part of the discharge opening 131 overlaps with the inlet chamber I and the wall section of the discharge opening 131 is positioned between them, the refrigerant in the inlet chamber I can exchange heat with the refrigerant in the discharge opening 131 through the wall section of the discharge opening 131 incorporated into the inlet chamber I. This means that the refrigerant in the inlet chamber I can be warmed by absorbing heat from the refrigerant in the discharge opening 131. This further prevents the liquid refrigerant from being injected into the compression chamber C through the injection hole 514.

[0144] Since at least part of the inlet opening 133 is incorporated into the discharge chamber D, that is, at least part of the inlet opening 133 overlaps with the discharge chamber D and the wall section of the inlet opening 133 is positioned between them, the refrigerant in the inlet opening 133 can exchange heat with the refrigerant in the discharge chamber D through the wall section of the inlet opening 133 incorporated into the discharge chamber D. This means that the refrigerant in the inlet opening 133 can be warmed by absorbing heat from the refrigerant in the discharge chamber D. This further prevents the liquid refrigerant from being injected into the compression chamber C through the injection hole 514.

[0145] Since the refrigerant at the discharge port 131 and the refrigerant at the inlet port 133 flow towards each other in a cross-flow direction, that is, the angle between the outlet of the discharge port 131 and the inlet of the inlet port 133 with respect to the center of the rear casing 130 is 0 degrees or more and less than 90 degrees, the refrigerant at the inlet port 133 can exchange heat with the refrigerant at the discharge port 131. In other words, the refrigerant at the inlet port 133 can be warmed by absorbing heat from the refrigerant at the discharge port 131. This more effectively prevents the injection of the liquid refrigerant through the injection port 514 into the compression chamber C.

[0146] The injector assembly 700 comprises the cover plate 710, the injector 720 and the valve plate 730, and the valve plate 730 not only forms part of the injection flow path, but also serves as a holder for the injector 720, that is, the valve plate 730 includes the chamfered space 734, so that the number of parts, the size, the cost and the weight of the injector assembly 700 can be reduced.

[0147] Since the injector 720 is designed such that the periphery 726 of the injector 720 is pressed and fixed between the cover plate 710 (more precisely, the injector sealing groove 710c) and the valve plate 730, a fastening element for attaching the injector 720 to at least one of the cover plate 710 and the valve plate 730 can be omitted. This allows the number of parts, the size, the cost, and the weight of the injector assembly 700 to be further reduced.

[0148] Since the injector assembly 700 is designed to be attached as a whole to the rear housing 130 by the fastening bolt 770, after being pre-aligned by the positioning pin 780, the properties and quality of the assembly can be improved.

[0149] Since the injection hole 514 is formed to communicate with the pair of compression chambers C simultaneously, that is, communication between the second injection hole 514b and the first inner compression chamber C12 begins when communication between the first injection hole 514a and the first outer compression chamber C11 begins, the pressure imbalance between the first outer compression chamber C11 and the first inner compression chamber C12 as well as abnormal behavior (e.g., overturning) of the spiral 400 can be prevented.

[0150] Since the injection hole 514 is also designed to be blocked simultaneously with the pair of compression chambers C, i.e., the communication between the second injection hole 514b and the first inner compression chamber C12 is terminated when the communication between the first injection hole 514a and the first outer compression chamber C11 is terminated, the pressure imbalance between the first outer compression chamber C11 and the first inner compression chamber C12 as well as abnormal behavior (e.g., overturning) of the spiral 400 can be further prevented.

[0151] The timing at which the injection port 514 communicates with the pair of compression chambers C, and the timing at which the injection port 514 is blocked simultaneously with the pair of compression chambers C, can be adjusted accordingly, taking into account the performance and efficiency of the scroll compressor.

[0152] On the other hand, in this embodiment, the injection valve assembly 700 is designed to branch the refrigerant flowing from the inlet chamber I into the angled space 734, directing it to the first injection hole 514a and the second injection hole 514b. That is to say, the inlet 712, the head 722 of the injection valve 720, the leg 724 of the injection valve 720, and the angled space 734 are each formed as one, and the connecting flow path 738 and the outlet 736 are formed as two.

[0153] In this embodiment, however, the flow velocities of the refrigerant distributed to the first injection hole 514a and the second injection hole 514b can differ. In particular, if the first connecting flow path 738a and the first outlet 736a are formed asymmetrically to the second connecting flow path 738b and the second outlet 736b, the flow velocity of the refrigerant distributed to the first injection hole 514a and the second injection hole 514b can become less uniform due to the different flow resistance.

[0154] In light of this, as in the Fig. 21, Fig. 22, Fig. 23 to Fig.Figure 24 shows an injection valve assembly 700 formed to direct a refrigerant flowing in from one side of an inlet chamber I to a first injection hole 514a, and can be formed to independently direct a refrigerant flowing in from the other side of an inlet chamber I to a second injection hole 514b.

[0155] In particular, inlet 712 may include a first inlet 712a, which communicates with one side of inlet chamber I, and a second inlet 712b, which is formed independently of the first inlet 712a and communicates with the other side of inlet chamber I.

[0156] Here it may be preferable for the first inlet 712a and the second inlet 712b to be formed in the form of long holes in order to maximize a valve lift force or a refrigerant inflow velocity.

[0157] The injector 720 can comprise a first head 722a that opens and closes the first inlet 712a, a first leg 724a that supports the first head 722a, a second head 722b that opens and closes the second inlet 712b, a second leg 724b that supports the second head 722b, and a periphery 726 that supports the first leg 724a and the second leg 724b.

[0158] Here, the first head 722a, the first leg 724a, the second head 722b, the second leg 724b and the periphery 726 can be formed integrally to reduce the number of parts, the size, the cost and the weight.

[0159] Furthermore, with regard to compactness, it may be preferable that the first leg 724a and the second leg 724b are formed parallel to each other, and that a connecting section between the first leg 724a and the periphery 726, as well as a connecting section between the second leg 724b and the periphery 726, are formed on opposite sides to each other. That is to say, it may be preferable that the first leg 724a and the second leg 724b are formed alternately.

[0160] The sloping space 734 can comprise a first sloping space 734a, which serves as a support for the first head 722a and receives the refrigerant flowing through the first inlet 712a, and a second sloping space 734b, which serves as a support for the second head 722b and receives the refrigerant flowing through the second inlet 712b.

[0161] Here it may be preferred that the first chamfered space 734a and the second chamfered space 734b are separated from each other, and it may be preferred that a mounting surface of the first chamfered space 734a and a mounting surface of the second chamfered space 734b are chamfered in alternating directions to correspond to the first leg 724a and the second leg 724b.

[0162] An outlet 736 can include a first outlet 736a that communicates with the first injection hole 514a, and a second outlet 736b that communicates with the second injection hole 514b, and a connecting flow path 738 can include a first connecting flow path 738a that connects the first chamfered space 734a and the first outlet 736a, and a second connecting flow path 738b that connects the second chamfered space 734b and the second outlet 736b.

[0163] Here, in the connection flow path 738 and the outlet 736, an inner diameter of the first connection flow path 738a can be formed to be larger than an inner diameter of the first outlet 736a, and an inner diameter of the second connection flow path 738b can be formed to be larger than an inner diameter of the second outlet 736b, so that no pressure loss and no flow velocity loss occurs while the refrigerant passes through the connection flow path 738 and the outlet 736.

[0164] In another embodiment of the present disclosure, since the refrigerant of the inlet chamber I is directed independently to the first injection hole 514a and the second injection hole 514b, the refrigerant is distributed equally to the first injection hole 514a and the second injection hole 514b.

[0165] On the other hand, the rotating spiral 400 and the stationary spiral 500 in the embodiment described above are designed to be received in the rear housing 130, but are not limited to this. That is to say, the stationary spiral 500 is designed to be free to the outside while it is arranged between the rear housing 130 and the central housing 110, and the rotating spiral 400 can be received in the stationary spiral 500.

Claims

[1] Scroll compressor, comprising: a case (100); a motor (200) provided in the housing (100); a rotating shaft (300) turned by the motor (200); a spiral winding (400) moved in a circular motion by the rotating shaft (300); and a stationary spiral (500) which together with the rotating spiral (400) forms a compression chamber (C), where the housing (100) has: a central housing (110) through which the rotating shaft (300) passes; a front housing (120) forming a motor mounting space (S1) in which the motor (200) is mounted; and a rear housing (130) comprising a discharge chamber (D) which receives a refrigerant discharged from the compression chamber (C), a discharge port (131) which directs the refrigerant from the discharge chamber (D) to the outside of the housing (100), an inlet port (133) into which a medium-pressure refrigerant is introduced from outside the housing (100), and an inlet chamber (I) which receives the refrigerant introduced through the inlet port (133), wherein at least part of the inlet chamber (I) is designed such that it is received in the ejection chamber (D), and wherein the stationary spiral (500) has an injection hole (514) which directs the refrigerant from the inlet chamber (I) to the compression chamber (C), wherein the rear housing (130) is integrally formed, and the rear housing (130) has: a first annular wall (134) located on the outermost side in the radial direction of the rear housing (130); a second annular wall (136) which is incorporated in the radial direction of the rear housing (130) in the first annular wall (134) and forms the ejection chamber (D); and a third annular wall (138) which is received in the radial direction of the rear housing (130) in the second annular wall (136) and forms the inlet chamber (I). [2] Scroll compressor according to claim 1, wherein at least a part of the inlet chamber (I) is formed to be received in the discharge chamber (D). [3] Scroll compressor according to claim 1, wherein the first annular wall (134), the second annular wall (136) and the third annular wall (138) have different heights. [4] Scroll compressor according to claim 1, wherein the second annular wall (136) is formed in contact with an outer circumference of a fixed base plate of the fixed spiral (500), and wherein the second annular wall (136) presses the fixed spiral (500) towards the central housing (110) when the rear housing (130) is coupled to the central housing (110). [5] Scroll compressor according to claim 1, wherein the third annular wall (138) is formed to be spaced apart from the stationary spiral (500). [6] Scroll compressor according to claim 5, wherein an injection valve assembly (700) which communicates and blocks between the inlet chamber (I) and the injection hole (514) is formed on an end surface of the third annular wall (138). [7] Scroll compressor according to claim 6, wherein the injection valve assembly (700) comprises: a cover plate (710) having an inlet (712) that communicates with the inlet chamber (I) and covers the inlet chamber (I); an injector (720) that opens and closes the inlet (712); and a valve plate (730) which has a beveled space (734) which serves as a holder for the injection valve (720) and receives the refrigerant flowing in through the inlet (712), and an outlet (736) which directs the refrigerant in the beveled space (734) to the injection hole (514). [8] Scroll compressor according to claim 6, wherein the stationary spiral (500) has a discharge hole (512) which discharges the refrigerant from the compression chamber (C) into the discharge chamber (D), and wherein a discharge valve (600) which opens and closes the discharge hole (512) is formed between the injection valve assembly (700) and the stationary spiral (500). [9] Scroll compressor according to claim 6, wherein the refrigerant directed into the injection hole (514) exchanges heat with the refrigerant in the discharge chamber (D) through the third annular wall (138) and the injection valve assembly (700). [10] Scroll compressor according to claim 1, wherein at least a part of the discharge opening (131) is formed to be received in the inlet chamber (I). [11] Scroll compressor according to claim 10, wherein the refrigerant of the inlet chamber (I) exchanges heat with the refrigerant of the outlet opening (131) through a wall of the outlet opening (131) received in the inlet chamber (I). [12] Scroll compressor according to claim 1, wherein at least a part of the inlet opening (133) is formed to be received in the discharge chamber (D). [13] Scroll compressor according to claim 12, wherein the refrigerant of the inlet opening (133) exchanges heat with the refrigerant of the discharge chamber (D) through a wall of the inlet opening (133) received in the discharge chamber (D).

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