Scroll Compressor

Abstract

To provide a scroll compressor that can prevent excessive compression.SOLUTION: In a scroll compressor, a discharge port 18 from which compressed fluid is discharged is formed in an end plate 15A of a fixed scroll 15, a center side compression chamber 17A communicating with the discharge port 18 is formed between an inside end part 15Ba of a spiral lap 15B and an inside end part 16Ba of a spiral lap 16B, a back side compression chamber 17B is formed between a back side of the spiral lap 15B and a ventral side of the spiral lap 16B, a ventral side compression chamber 17C is formed between a ventral side of the spiral lap 15B and a back side of the spiral lap 16B, a cutout part 15Bb causing the center side compression chamber 17A and the back side compression chamber 17B to communicate with each other is formed on a back side of a tooth crest surface opposed to an end plate, and a cutout part 16Bb causing the center side compression chamber 17A and the ventral side compression chamber 17C to communicate with each other is formed on a back side of a tooth crest surface opposed to the end plate 15A.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present disclosure relates to scroll compressors. [Background technology]

[0002] The scroll compressor has a pair of fixed scrolls and an orbiting scroll, each with a spiral wrap standing on its end plate, and is configured to compress refrigerant gas by moving the compression chamber formed by the meshing of the two scrolls from the outer periphery toward the center as the orbiting scroll revolves, reducing its volume, and then discharge the high-pressure gas into a discharge chamber from a discharge port provided in the center of the fixed scroll (see, for example, Patent Document 1).

[0003] The scroll compressor is configured so that the compression chambers are gradually moved toward the center as the orbiting scroll is driven to orbit, reducing their volume, and has a design volume ratio (operating pressure ratio) defined as the ratio between the maximum compression chamber volume formed at the outermost positions of both scrolls at the time of suction shutoff and the minimum compression chamber volume immediately before the fixed scroll and orbiting scroll disengage.

[0004] In Patent Document 1, a protruding wall is provided on the back wall of the inner peripheral end of the spiral wrap of the orbiting scroll. The provision of the protruding wall delays the timing at which the back wall crosses the discharge port provided in the fixed scroll and connects the compression chamber one outside the central compression chamber to the discharge port, thereby reducing the minimum compression chamber volume and increasing the design volume ratio. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Laid-Open No. 2013-181487 Summary of the Invention [Problem to be solved by the invention]

[0006] However, in conventional scroll compressors, the design pressure ratio is determined by the shape of the scroll. Therefore, if the operating pressure ratio is lower than the design pressure ratio, excessive compression occurs, in which the fluid inside the scroll compressor becomes higher than the discharge pressure, resulting in a loss of compression power and a decrease in operating efficiency.

[0007] The present disclosure has been made in view of the above circumstances, and has an object to provide a scroll compressor that can prevent excessive compression. [Means for solving the problem]

[0008] In order to solve the above problems, the scroll compressor of the present disclosure employs the following measures. A scroll compressor according to one aspect of the present disclosure includes a fixed scroll having a first spiral wall body standing on one side surface of a first end plate, and an orbiting scroll having a second spiral wall body standing on one side surface of a second end plate, the orbiting scroll being supported so as to be capable of orbital movement while being meshed with the first wall body and prevented from rotating on its own axis, wherein a discharge port is formed in the first end plate of the fixed scroll, through which fluid compressed by the fixed scroll and the orbiting scroll is discharged, and a center-side compression chamber communicating with the discharge port is formed between a first inner end portion of the first wall body and a second inner end portion of the second wall body. a dorsal compression chamber adjacent to the central compression chamber is formed between the dorsal side of the first wall body and the ventral side of the second wall body, and a ventral compression chamber adjacent to the central compression chamber is formed between the ventral side of the first wall body and the dorsal side of the second wall body; at the first inner end of the first wall body, a first notch is formed on the dorsal side of a first tip surface facing the second end plate, which connects the central compression chamber and the ventral compression chamber; and at the second inner end of the second wall body, a second notch is formed on the dorsal side of a second tip surface facing the first end plate, which connects the central compression chamber and the ventral compression chamber. [Effects of the Invention]

[0009] According to the present disclosure, it is possible to provide a scroll compressor that can prevent excessive compression. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure. FIG. [Figure 2] 2 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the line AA. [Figure 3] 2 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the arrow BB. [Figure 4] 3 is a cross-sectional view of the scroll compressor shown in FIG. 2 taken along the arrow CC. [Figure 5] 2 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the line AA, showing a state after a predetermined time has elapsed since FIG. [Figure 6] 4 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the arrow BB, showing a state after a predetermined time has elapsed since FIG. 3. [Figure 7] 5 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the line AA, showing a state after a predetermined time has elapsed since FIG. [Figure 8] 6 is a cross-sectional view of the scroll compressor shown in FIG. 1 taken along the arrow BB, showing a state after a predetermined time has elapsed since FIG. DETAILED DESCRIPTION OF THE INVENTION

[0011] A scroll compressor 1 according to an embodiment of the present disclosure will be described below with reference to the drawings. The scroll compressor 1 of this embodiment is used, for example, as a refrigeration cycle (not shown) including a plurality of scroll compressors 1 connected in series. This refrigeration cycle repeats the steps of compressing a low-temperature, low-pressure gas-phase refrigerant (fluid) evaporated in an evaporator (not shown) in stages using the plurality of scroll compressors 1 to form a high-temperature, high-pressure gas-phase refrigerant, dissipating heat in a condenser (not shown) to form a high-temperature, high-pressure liquid-phase refrigerant, and reducing the pressure in an expansion valve (not shown) to form a low-temperature, low-pressure liquid-phase refrigerant.

[0012] In this refrigeration cycle, the refrigerant is compressed by multiple scroll compressors 1 (for example, two units), and therefore the operating pressure ratio of each scroll compressor 1 is lower than the desired operating pressure ratio required for the refrigeration cycle. Therefore, if the operating pressure ratio of each scroll compressor 1 is lower than the design pressure ratio, excessive compression occurs, in which the refrigerant in the scroll compressor 1 becomes higher than the discharge pressure, resulting in a loss of compression power and a decrease in operating efficiency. Therefore, the scroll compressor 1 of this embodiment employs a configuration that suppresses excessive compression.

[0013] The scroll compressor 1 of this embodiment will be described in detail below. As shown in Fig. 1, scroll compressor 1 includes housings 2A and 2B that form an outer shell. Housings 2A and 2B are sealed cylindrical and form a sealed space inside. A scroll compression mechanism 5, a drive shaft 6, an electric motor 7, and a bearing 8 are incorporated in the sealed space.

[0014] The sealed space corresponding to housing 2A is a discharge chamber CB1, and the sealed space corresponding to housing 2B is a suction chamber CB2. A discharge pipe 31 for discharging the refrigerant is provided on the upper wall of housing 2A, connecting discharge chamber CB1 to the outside of housing 2A. A suction pipe 32 for drawing in the refrigerant is provided on the side wall of housing 2B, connecting suction chamber CB2 to the outside of housing 2B.

[0015] The scroll compression mechanism 5 is a device that compresses and discharges a refrigerant, and is connected to a drive shaft 6 driven by an electric motor 7. The drive shaft 6 is rotatably supported in the housing 2B via a bearing 8. A crank pin 13 is integrally provided at the rear end of the drive shaft 6, and is eccentric by a predetermined dimension in a direction perpendicular to the axis X, which is the central axis of the drive shaft 6. The crank pin 13 is connected to an orbiting scroll 16 of the scroll compression mechanism 5 via a known driven crank mechanism 14 that includes a drive bushing and a drive bearing that change the orbital radius of the orbiting scroll 16.

[0016] The scroll compression mechanism 5 has a pair of fixed scrolls 15 and orbiting scrolls 16 meshed with each other with a phase shift of 180°, thereby forming a pair of compression chambers 17 between the fixed scroll 15 and the orbiting scroll 16 that face each other across the center of the fixed scroll 15. The scroll compression mechanism 5 compresses the refrigerant gas by moving the compression chambers 17 from an outer periphery position to a central position while gradually reducing their volume.

[0017] The fixed scroll 15 has a spiral wrap (first wall) 15B, which is a wall provided on one side of an end plate (first end plate) 15A. A discharge port 18 is formed in the end plate 15A, through which the refrigerant gas compressed by the fixed scroll 15 and the orbiting scroll 16 is discharged. The fixed scroll 15 is fixed to a discharge cover 3 sandwiched between the housings 2A and 2B.

[0018] The orbiting scroll 16 has a spiral wrap (second wall) 16B, which is a wall erected on one side of an end plate (second end plate) 16A. The orbiting scroll 16 is connected to a crank pin 13 of the drive shaft 6 via a driven crank mechanism 14, and is supported on a thrust bearing surface of the housing 2B via a known rotation-preventing mechanism (not shown) so as to be capable of orbital movement. The orbiting scroll 16 is meshed with the spiral wrap 15B of the fixed scroll 15, so as to be prevented from rotating on its own axis, but is supported so as to be capable of orbital movement.

[0019] The tooth tip surface (first tip surface) 15C of the fixed scroll 15 faces the tooth bottom surface (one side surface) 16D of the orbiting scroll 16, and the tooth tip surface (second tip surface) 16C of the orbiting scroll 16 faces the tooth bottom surface 15D of the fixed scroll 15. A discharge cover 3 is disposed above the fixed scroll 15 (on the back surface of the end plate 15A), and defines a back pressure chamber CB3 together with the back surface of the end plate 15A.

[0020] A discharge port 18 that connects the compression chamber 17 and the back pressure chamber CB3 is formed in the end plate 15A. A discharge port 3A that connects the back pressure chamber CB3 and the discharge chamber CB1 is formed in the discharge cover 3. The compression chamber 17 and the discharge chamber CB1 are in communication via the discharge port 18, the back pressure chamber CB3, and the discharge port 3A.

[0021] Discharge chamber CB1 is provided at the outlet of discharge port 3A with a reed valve 92 and a retainer 93 that restricts the range of movement of reed valve 92. Refrigerant pressurized to a predetermined pressure in compression chamber 17 flows from discharge port 18 into back pressure chamber CB3, is guided from discharge port 3A via reed valve 92 to discharge chamber CB1, and is then discharged from discharge pipe 31 to the outside.

[0022] Next, the notch 15Bb formed on the tooth tip surface 15C of the spiral wrap 15B of the fixed scroll 15 and the notch 16Bb formed on the tooth tip surface 16C of the spiral wrap 16B of the orbiting scroll 16 will be described with reference to the drawings.

[0023] Figures 2 and 3 are cross-sectional views taken along the lines AA and BB of the scroll compressor shown in Figure 1. Figure 4 is a cross-sectional view taken along the line CC of the scroll compressor shown in Figure 2. Figures 5 and 6 are cross-sectional views taken along the lines AA and BB of the scroll compressor shown in Figure 1, showing a state a predetermined time has elapsed since Figures 2 and 3. Figures 7 and 8 are cross-sectional views taken along the lines AA and BB of the scroll compressor shown in Figure 1, showing a state a predetermined time has elapsed since Figures 5 and 6.

[0024] 2 to 7, the compression chamber 17 shown in Fig. 1 has a center-side compression chamber 17A, a dorsal-side compression chamber 17B, and a ventral-side compression chamber 17C. The center-side compression chamber 17A is a compression chamber formed between the inner end (first inner end) 15Ba of the spiral wrap 15B and the inner end (second inner end) 16Ba of the spiral wrap 16B, and is in communication with the discharge port 18.

[0025] Dorsal compression chamber 17B is a compression chamber formed between the dorsal side of spiral wrap 15B and the ventral side of spiral wrap 16B, and is adjacent to central compression chamber 17A. Ventral compression chamber 17C is a compression chamber formed between the ventral side of spiral wrap 15B and the dorsal side of spiral wrap 16B, and is adjacent to central compression chamber 17A.

[0026] 2, 5, and 7, end plate 15A is formed with a plurality of bypass ports 19A each having a valve that opens when the pressure of the refrigerant gas in ventral compression chamber 17C exceeds a predetermined pressure. Bypass ports 19A discharge refrigerant gas at a pressure above a predetermined pressure before the refrigerant gas is discharged from discharge port 18, thereby preventing excessive compression.

[0027] 2, 5, and 7, end plate 15A is formed with a plurality of bypass ports 19B each having a valve that opens when the pressure of the refrigerant gas in back compression chamber 17B exceeds a predetermined pressure. Bypass ports 19B discharge refrigerant gas at a pressure above a predetermined pressure before the refrigerant gas is discharged from discharge port 18, thereby preventing excessive compression.

[0028] At the inner end 15Ba of the spiral wrap 15B, a notch (first notch) 15Bb that connects the center-side compression chamber 17A and the back-side compression chamber 17B is formed on the back side of the tooth tip surface 15C that faces the end plate 16A. As shown in Fig. 4, the notch 15Bb is a cutout portion that is formed in the horizontal direction HD perpendicular to the axis X so that the width W2 of the spiral wrap 15B adjacent to the tooth tip surface 15C is narrower than the width W1 of the spiral wrap 15B adjacent to the tooth bottom surface 15D of the fixed scroll 15.

[0029] The cutout 15Bb has a constant width (W1-W2 in FIG. 4) along the vertical direction VD parallel to the axis X. The height H2 of the cutout 15Bb in the vertical direction VD is greater than the height H1 of the spiral wrap 15B excluding the cutout 15Bb in the vertical direction VD. The height H2 is set to, for example, about twice the height H1.

[0030] The cutout portion 15Bb is provided to accelerate the timing of connecting the back compression chamber 17B and the center compression chamber 17A compared to a spiral wrap 15B (having the same width in the horizontal direction HD at each position in the vertical direction VD) in which the cutout portion 15Bb is not formed.

[0031] At the inner end 16Ba of the spiral wrap 16B, a notch (second notch) 16Bb that connects the center-side compression chamber 17A and the ventral-side compression chamber 17C is formed on the ventral side of the tooth tip surface 16C that faces the end plate 15A. Also, at the inner end 16Ba of the spiral wrap 16B, a notch 16Bc is formed on the ventral side of the tooth tip surface 16C that faces the end plate 15A.

[0032] As shown in FIG. 4, the notch 16Bb and the notch 16Bc are cut out in a horizontal direction HD perpendicular to the axis X so that the width W4 of the spiral wrap 16B adjacent to the tooth tip surface 16C is narrower than the width W3 of the spiral wrap 16B adjacent to the tooth bottom surface 16D of the orbiting scroll 16.

[0033] The notch 16Bb has a constant width along the vertical direction VD parallel to the axis X. The height H4 of the notch 16Bb in the vertical direction VD is greater than the height H3 of the spiral wrap 16B in the vertical direction VD excluding the notch 16Bb and the notch 16Bc. The height H4 is set to, for example, about twice the height H3.

[0034] The cutout portion 16Bb is provided to accelerate the timing at which the ventral side compression chamber 17C and the central side compression chamber 17A communicate with each other, compared to a spiral wrap 16B in which the cutout portion 16Bb is not formed.

[0035] Here, the timing at which back-side compression chamber 17B and central-side compression chamber 17A communicate with each other via cutout 15Bb, and the timing at which ventral-side compression chamber 17C and central-side compression chamber 17A communicate with each other via cutout 16Bb will be described.

[0036] 2 and 3 show an operating state in which the volume of center-side compression chamber 17A gradually decreases, and center-side compression chamber 17A does not communicate with dorsal-side compression chamber 17B or ventral-side compression chamber 17C. As shown in FIGS. 2 and 3, the ventral side of spiral wrap 15B and the dorsal side of spiral wrap 16B come into contact at meshing point P1, and the dorsal side of spiral wrap 15B and the ventral side of spiral wrap 16B come into contact at meshing point P2. Meshing point P1 is located in an area where notch 16Bb of spiral wrap 16B does not exist, and meshing point P2 is located in an area where notch 15Bb of spiral wrap 15B does not exist.

[0037] 2 and 3, the state shown in Figures 5 and 6 is reached. Figures 5 and 6 show an operating state in which the volume of center-side compression chamber 17A gradually decreases, and show a state in which center-side compression chamber 17A begins to communicate with both dorsal compression chamber 17B and ventral compression chamber 17C. As shown in Figures 5 and 6, meshing point P1 is located in the area where notch 16Bb of spiral wrap 16B is present, and meshing point P2 is located in the area where notch 15Bb of spiral wrap 15B is present.

[0038] 5 and 6 show the timing immediately after communication between central compression chamber 17A and dorsal compression chamber 17B begins and communication between central compression chamber 17A and ventral compression chamber 17C begins. As shown in Figures 5 and 6, cutouts 15Bb and 16Bb are formed so that the timing at which communication between central compression chamber 17A and ventral compression chamber 17C begins via cutout 16Bb coincides with the timing at which communication between central compression chamber 17A and dorsal compression chamber 17B begins via cutout 15Bb.

[0039] 5, when communication between the central compression chamber 17A and the dorsal compression chamber 17B begins and communication between the central compression chamber 17A and the ventral compression chamber 17C begins, communication between the discharge port 18 and the ventral compression chamber 17C begins at communication point P3. That is, the discharge port 18 is formed in the end plate 15A so that the timing when communication between the central compression chamber 17A and the ventral compression chamber 17C begins via the cutout portion 16Bb coincides with the timing when direct communication between the discharge port 18 and the ventral compression chamber 17C begins.

[0040] When communication between center-side compression chamber 17A and back-side compression chamber 17B begins, refrigerant gas flows from back-side compression chamber 17B to center-side compression chamber 17A through cutout 15Bb, reducing the pressure in back-side compression chamber 17B. Also, refrigerant gas flows from ventral compression chamber 17C to center-side compression chamber 17A through cutout 16Bb, reducing the pressure in ventral compression chamber 17C.

[0041] When a predetermined time has passed from the state shown in Figures 5 and 6, the state shown in Figures 7 and 8 is reached. Figures 7 and 8 show an operating state in which the volume of central compression chamber 17A gradually decreases, and central compression chamber 17A is in communication with both dorsal compression chamber 17B and ventral compression chamber 17C.

[0042] 7 and 8, meshing point P1 is located in the region where notch 16Bb of spiral wrap 16B is present, and meshing point P2 is located in the region where notch 15Bb of spiral wrap 15B is present. As shown in Fig. 7, discharge port 18 is formed in end plate 15A so as to directly communicate with ventral-side compression chamber 17C, with central-side compression chamber 17A and ventral-side compression chamber 17C communicating with each other via cutout 16Bb.

[0043] The scroll compressor 1 of the present embodiment described above provides the following functions and effects. In the scroll compressor 1 of this embodiment, a notch 15Bb that connects the center-side compression chamber 17A and the back-side compression chamber 17B is formed on the back side of the tooth crest 15C of the inner end 15Ba of the spiral wrap 15B of the fixed scroll 15, the tooth crest 15C facing the end plate 16A of the orbiting scroll 16. Therefore, as the volume of the center-side compression chamber 17A gradually decreases, the timing at which the center-side compression chamber 17A and the back-side compression chamber 17B begin to communicate with each other is earlier than when the notch 15Bb is not formed. This makes it possible to suppress excessive compression in the back-side compression chamber 17B.

[0044] Furthermore, in the scroll compressor 1 of this embodiment, a notch 16Bb that connects the center-side compression chamber 17A and the pressure-side compression chamber 17C is formed on the back side of the tooth crest 16C of the inner end 16Ba of the spiral wrap 16B of the orbiting scroll 16, the tooth crest 16C facing the end plate 15A of the fixed scroll 15. Therefore, as the volume of the center-side compression chamber 17A gradually decreases, the timing at which the center-side compression chamber 17A and the pressure-side compression chamber 17C begin to communicate with each other is earlier than when the notch 16Bb is not formed. As a result, excessive compression in the pressure-side compression chamber 17C can be suppressed.

[0045] Furthermore, according to the scroll compressor 1 of this embodiment, the central compression chamber 17A and the abdominal compression chamber 17C are in communication with each other via the cutout 16Bb, and the discharge port 18 is in direct communication with the abdominal compression chamber 17C. Therefore, the refrigerant gas compressed in the abdominal compression chamber 17C is guided directly to the discharge port 18 and also guided from the cutout 16Bb to the discharge port 18 via the central compression chamber 17A. By guiding the refrigerant gas compressed in the abdominal compression chamber 17C to the discharge port 18 via two paths, excessive compression in the abdominal compression chamber 17C can be reliably suppressed.

[0046] According to the scroll compressor 1 of this embodiment, the timing at which the central compression chamber 17A and the ventral compression chamber 17C start to communicate with each other coincides with the timing at which the discharge port 18 and the ventral compression chamber 17C start to communicate with each other. This ensures a sufficient flow path cross-sectional area for the refrigerant gas when the ventral compression chamber 17C starts to communicate with the discharge port 18, thereby suppressing the occurrence of pressure loss of the refrigerant gas.

[0047] According to the scroll compressor 1 of this embodiment, the timing at which the central compression chamber 17A and the pressure-side compression chamber 17C start to communicate with each other coincides with the timing at which the central compression chamber 17A and the back-side compression chamber 17B start to communicate with each other. This suppresses twisting in the direction opposite to the rotation direction of the orbiting scroll 16, which is caused by a pressure difference between the back-side compression chamber 17B and the pressure-side compression chamber 17C. This prevents loss reduction due to leakage of refrigerant gas inside the scroll compression mechanism 5 and prevents abnormal noise caused by refrigerant gas leakage.

[0048] The scroll compressor according to the embodiment of the present disclosure described above can be understood, for example, as follows. A scroll compressor (1) according to one aspect of the present disclosure includes: a fixed scroll (15) having a spiral-shaped first wall body (15B) erected on one side surface of a first end plate (15A); and an orbiting scroll (16) having a spiral-shaped second wall body (16B) erected on one side surface of a second end plate (16A), the orbiting scroll (16) being supported so as to be capable of orbital movement while being meshed with the first wall body and prevented from rotating on its axis, wherein a discharge port (18) is formed in the first end plate of the fixed scroll, through which a fluid compressed by the fixed scroll and the orbiting scroll is discharged; and a center-side compression valve (16) communicating with the discharge port is formed between a first inner end portion (15Ba) of the first wall body and a second inner end portion (16Ba) of the second wall body. A chamber (17A) is formed, a dorsal compression chamber (17B) adjacent to the central compression chamber is formed between the dorsal side of the first wall body and the ventral side of the second wall body, a ventral compression chamber (17C) adjacent to the central compression chamber is formed between the ventral side of the first wall body and the dorsal side of the second wall body, at the first inner end of the first wall body, a first notch (15Bb) connecting the central compression chamber and the ventral compression chamber is formed on the dorsal side of a first tip face (15C) facing the second end plate, and at the second inner end of the second wall body, a second notch (16Bb) connecting the central compression chamber and the ventral compression chamber is formed on the dorsal side of a second tip face (16C) facing the first end plate.

[0049] In a scroll compressor according to one aspect of the present disclosure, a first notch that connects the center-side compression chamber and the back-side compression chamber is formed on the back side of the first tip surface of the first inner end portion of the first wall of the fixed scroll, the first notch being in communication with the back-side compression chamber. Therefore, as the volume of the center-side compression chamber gradually decreases, the timing at which the center-side compression chamber and the back-side compression chamber begin to communicate with each other is earlier than when the first notch is not formed. This makes it possible to suppress excessive compression in the back-side compression chamber.

[0050] In addition, in a scroll compressor according to one aspect of the present disclosure, a second notch that connects the central compression chamber and the ventral compression chamber is formed on the back side of the second tip face of the second inner end portion of the second wall of the orbiting scroll, the second notch being in communication with the ventral compression chamber. Therefore, as the volume of the central compression chamber gradually decreases, the timing at which the central compression chamber and the ventral compression chamber begin to communicate with each other is earlier than when the second notch is not formed. This makes it possible to prevent excessive compression in the ventral compression chamber.

[0051] In a scroll compressor according to one embodiment of the present disclosure, the discharge port may be configured to be formed in the first end plate so as to be directly connected to the ventral compression chamber, with the central compression chamber and the ventral compression chamber connected via the second cutout portion.

[0052] In this scroll compressor, the central compression chamber and the ventral compression chamber are in communication with each other through the second notch, and the discharge port is in direct communication with the ventral compression chamber. Therefore, fluid compressed in the ventral compression chamber is guided directly to the discharge port and also to the discharge port via the second notch and the central compression chamber. By guiding the fluid compressed in the ventral compression chamber to the discharge port through two paths, excessive compression in the ventral compression chamber can be reliably suppressed.

[0053] In the scroll compressor having the above configuration, the discharge port may be formed in the first end plate so that the timing at which the central compression chamber and the ventral compression chamber start to communicate with each other via the second notch coincides with the timing at which the discharge port and the ventral compression chamber start to communicate with each other.

[0054] In the scroll compressor of this aspect, the timing at which the central compression chamber and the ventral compression chamber start to communicate with each other coincides with the timing at which the discharge port and the ventral compression chamber start to communicate with each other, thereby ensuring a sufficient cross-sectional area of ​​the fluid flow path when the ventral compression chamber and the discharge port start to communicate with each other, and suppressing the occurrence of pressure loss of the fluid.

[0055] In a scroll compressor according to one embodiment of the present disclosure, the first notch and the second notch may be formed so that the timing at which the center-side compression chamber and the ventral compression chamber start to communicate with each other through the second notch coincides with the timing at which the center-side compression chamber and the stern-side compression chamber start to communicate with each other through the first notch.

[0056] In the scroll compressor having this configuration, the timing at which the central compression chamber and the ventral compression chamber begin to communicate with each other coincides with the timing at which the central compression chamber and the suction chamber begin to communicate with each other, thereby preventing problems caused by a pressure difference between the suction chamber and the suction chamber. [Explanation of symbols]

[0057] 1 Scroll compressor 2A, 2B housing 3A discharge port 5 Scroll compression mechanism 6 drive shaft 7 Electric motor 15 Fixed Scroll 15A End plate (1st end plate) 15B Spiral wrap (first wall) 15Ba Inner end (first inner end) 15Bb Notch (First notch) 15C Tooth tip surface (first tip surface) 15D bottom surface 16 Swivel Scroll 16A End plate (2nd end plate) 16B Spiral wrap (second wall) 16Ba inner end (second inner end) 16Bb Notch (Second notch) 16Bc Notch 16C Tooth tip surface (second tip surface) 16D bottom surface 17 Compression chamber 17A Center compression chamber 17B Back compression chamber 17C Ventral compression chamber 18 Discharge port HD horizontal P1 Engagement point P2 meshing point P3 communication point VD vertical direction X axis

Claims

1. a fixed scroll having a spiral-shaped first wall body erected on one side surface of a first end plate; a second wall body having a spiral shape erected on one side surface of the second end plate, and an orbiting scroll supported by the first wall body so as to be prevented from rotating on its own axis and to be capable of orbiting; a discharge port through which fluid compressed by the fixed scroll and the orbiting scroll is discharged is formed in the first end plate of the fixed scroll, a center-side compression chamber communicating with the discharge port is formed between a first inner end portion of the first wall body and a second inner end portion of the second wall body; a back-side compression chamber adjacent to the center-side compression chamber is formed between the back side of the first wall body and the ventral side of the second wall body, a ventral compression chamber adjacent to the central compression chamber is formed between the ventral side of the first wall body and the dorsal side of the second wall body, a first notch portion that communicates the center-side compression chamber and the rear-side compression chamber is formed on a rear side of a first tip end surface that faces the second end plate at the first inner end portion of the first wall body, a second notch portion that communicates the central compression chamber with the ventral compression chamber is formed on a dorsal side of a second tip end surface that faces the first end plate at the second inner end portion of the second wall body, a height of the first cutout portion is greater than a height of the first wall body excluding the first cutout portion; A scroll compressor, wherein the height of the second cutout portion is greater than the height of the second wall body excluding the portion of the second cutout portion.

2. 2. The scroll compressor according to claim 1, wherein the discharge port is formed in the first end plate so as to directly communicate with the ventral-side compression chamber, with the central-side compression chamber and the ventral-side compression chamber communicating with each other via the second cutout portion.

3. 3. The scroll compressor according to claim 2, wherein the discharge port is formed in the first end plate so that a timing at which the central compression chamber and the ventral compression chamber start to communicate with each other via the second cutout coincides with a timing at which the discharge port and the ventral compression chamber start to communicate with each other.

4. 4. The scroll compressor according to claim 1, wherein the first notch and the second notch are formed so that a timing at which the center-side compression chamber and the ventral-side compression chamber start to communicate with each other via the second notch coincides with a timing at which the center-side compression chamber and the suction-side compression chamber start to communicate with each other via the first notch.

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