Scroll compressor

Abstract

The present invention provides a scroll compressor that ensures lubrication to the Oldham ring and suppresses a decrease in compression efficiency under low pressure ratio conditions. [Solution] The scroll compressor 100 comprises a spiral scroll 1 having a spiral spiral wrap 1a, a fixed scroll 2 having a spiral fixed wrap 2a, a frame 5 supporting the fixed scroll 2, an intake chamber 12 for drawing in refrigerant, a compression chamber 3 formed between the spiral wrap 1a and the fixed wrap 2a for compressing the refrigerant, a back pressure chamber 6 formed between the spiral scroll 1 and the frame 5, compression-side communication passages 8a and 8b that intermittently connect the compression chamber 3 and the back pressure chamber 6, and an intake-side communication passage 13 for intermittently connecting the intake chamber 12 and the back pressure chamber 6, wherein the timing of the suction-side communication passage 13 is different from the timing of the compression-side communication passage.

Description

Technical Field

[0001] The present disclosure relates to a scroll compressor.

Background Art

[0002] In compressors for computer air conditioners, VRF compressors, etc., operation under low pressure ratio conditions is required. In operation under low pressure ratio conditions, the differential pressure between the pressure in the back pressure chamber and the discharge pressure tends to be small. When this differential pressure is small, it becomes difficult to supply oil to the oldham ring.

[0003] Patent Document 1 discloses a scroll compressor provided with opening and closing means for a passage that connects the back pressure chamber and the suction chamber when the pressure difference between the pressure in the back pressure chamber and the discharge pressure becomes less than the pressure difference (oil supply differential pressure) required to supply oil to the oldham ring. When the oil supply differential pressure becomes small, the opening and closing means opens, and by releasing the pressure in the back pressure chamber to the suction chamber, it becomes possible to ensure the oil supply differential pressure to the oldham ring.

[0004] The above scroll compressor has pores provided in the mirror plate of the orbiting scroll, and these pores communicate with the back pressure chamber formed by the orbiting scroll and the frame. As a result, the gas refrigerant inside the scroll is guided to the back pressure chamber, and an upward pushing force is applied to the back surface of the orbiting scroll by the gas refrigerant at an intermediate pressure (the pressure between the suction pressure (low pressure side pressure) and the discharge pressure), counteracting the thrust direction force (the separating force that tries to push the orbiting scroll downward) due to the compression pressure in the plurality of compression chambers formed by the orbiting scroll and the fixed scroll.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] The valve body, which is the opening and closing mechanism of the scroll compressor described above, is open when the pressure in the back pressure chamber is greater than the discharge pressure (operating conditions with a low pressure ratio), and the gaseous refrigerant in the back pressure chamber flows into the suction chamber regardless of the crank angle. Therefore, there is a risk that the gaseous refrigerant will flow into the back pressure chamber through the pores during compression and then flow from the back pressure chamber into the suction chamber, which may reduce the compression efficiency.

[0007] The purpose of this disclosure is to provide a scroll compressor that can ensure lubrication to the Oldham ring and suppress a decrease in compression efficiency under low pressure ratio conditions. [Means for solving the problem]

[0008] The scroll compressor of this disclosure comprises an orbiting scroll having a spiral orbiting wrap and a stationary scroll having a spiral orbiting wrap; a frame supporting the stationary scroll; an intake chamber for drawing in a refrigerant; a compression chamber formed between the orbiting wrap and the stationary wrap for compressing the refrigerant; a back pressure chamber formed between the orbiting scroll and the frame; a compression-side communication passage intermittently connecting the compression chamber and the back pressure chamber; and an intake-side communication passage for intermittently connecting the intake chamber and the back pressure chamber, wherein the timing of the suction-side communication passage is different from the timing of the compression-side communication passage. [Brief explanation of the drawing]

[0009] [Figure 1] Figure 1 shows a portion of the longitudinal cross-section of a scroll compressor according to one embodiment. [Figure 2] Figure 2 is a bottom view showing the fixed scroll of the scroll compressor according to the same embodiment. [Figure 3] Figure 3 shows a portion of the vertical cross-section of a scroll compressor according to the same embodiment. [Figure 4] Figure 4 shows a portion of the vertical cross-section of a scroll compressor according to the same embodiment. [Figure 5] Figure 5 is an enlarged view of the valve body portion shown in Figure 1. [Figure 6]Figure 6 shows a portion of the longitudinal cross-section of a scroll compressor according to another embodiment. [Modes for carrying out the invention]

[0010] A scroll compressor 100 according to one embodiment will be described with reference to Figures 1 to 5. Note that the dimensional ratios in the drawings do not necessarily match the actual dimensional ratios, and the dimensional ratios between the drawings do not necessarily match either. Figures 1, 3, and 4 show a part of the longitudinal cross-section of the scroll compressor 100, Figure 2 is a bottom view showing the fixed scroll 2 of the scroll compressor 100, and Figure 5 is an enlarged view of the valve body 16 portion of Figure 1.

[0011] As shown in Figure 1, the scroll compressor 100 (hereinafter also simply referred to as "compressor 100") is configured to compress the refrigerant. The compressor 100 is used, for example, in large commercial air conditioners such as VRFs and computer air conditioners.

[0012] The compressor 100 comprises a sealed container (not shown), a rotating scroll 1, a fixed scroll 2, a frame 5, an Oldham ring 11, a crankshaft (not shown), and an electric motor (not shown).

[0013] The sealed container is a cylindrical container that houses the orbiting scroll 1, the stationary scroll 2, the frame 5, the Oldham ring 11, the crankshaft, and the electric motor, and is substantially sealed. The sealed container is filled with lubricating oil to enhance the lubrication of the compressor 100, and is stored as an oil reservoir at the bottom of the sealed container.

[0014] The sealed container comprises a cylindrical chamber, a lid chamber fixed to the upper part of the cylindrical chamber, and a bottom chamber fixed to the lower part of the cylindrical chamber. An intake pipe (not shown) is inserted into and fixed to the lid chamber of the sealed container. The intake pipe is a tube that guides the refrigerant to the intake chamber 12, which will be described later. A discharge pipe (not shown) is inserted into and fixed to the cylindrical chamber of the sealed container. The discharge pipe is a tube that guides the gaseous refrigerant (also called gaseous refrigerant) compressed in the compression chamber 3, which will be described later, to the outside of the compressor 100.

[0015] The crankshaft is a shaft that rotates integrally with the rotor of the electric motor and extends vertically. The crankshaft is fixed coaxially to the rotor of the electric motor. Inside the crankshaft, there is a lubrication passage through which lubricating oil flows, and this lubrication passage extends vertically. The lubrication passage is immersed in lubricating oil accumulated in an oil reservoir, and the lubricating oil flows through the lubrication passage (drawn up) due to the pressure difference (lubrication differential pressure) between the discharge pressure and the pressure in the back pressure chamber 6 described later. The lubricating oil that has flowed to the top of the lubrication passage is supplied to the Oldham ring 11, the crankshaft bearings, etc.

[0016] The electric motor is the drive source that rotates the crankshaft and is located on the underside of the frame 5. The electric motor comprises a stator and a rotor. The stator is a cylindrical member made of laminated electromagnetic steel sheets and is fixed to the inner circumferential wall of the cylindrical chamber. The rotor is a cylindrical member made of laminated electromagnetic steel sheets and is positioned radially inward of the stator. The rotor is fixed to the crankshaft by press-fitting or other means.

[0017] The orbiting scroll 1 and the fixed scroll 2 are located in the upper space of the sealed container. The fixed scroll 2 is a fixed member fixed within the sealed container, while the orbiting scroll 1 is a movable (orbiting) member that forms a compression chamber 3 between itself and the fixed scroll 2 through its orbit.

[0018] The orbiting scroll 1 is provided between the stationary scroll 2 and the frame 5. The orbiting scroll 1 includes a spiral orbiting wrap 1a, a disk-shaped orbiting base plate 1b, and a boss portion (not shown) that fits onto the upper end of the crankshaft. The orbiting wrap 1a stands upright above the orbiting base plate 1b.

[0019] The stationary scroll 2 includes a spiral stationary wrap 2a and a disk-shaped thick stationary base plate 2b. The stationary wrap 2a stands upright below the stationary base plate 2b. An intake chamber 12 having an inlet through which gas refrigerant is inhaled from an intake pipe is provided on the peripheral side of the stationary base plate 2b. A discharge port for guiding the gas refrigerant compressed in the compression chamber 3 to the upper space inside the sealed container is provided at the center of the stationary base plate 2b of the stationary scroll 2.

[0020] The compression chamber 3 is formed between the orbiting wrap 1a and the stationary wrap 2a by meshing them together, and is a space for compressing the gas refrigerant. The compression chamber 3 consists of an outer line chamber 3a formed on the outer line side of the orbiting wrap 1a and an inner line chamber 3b formed on the inner line side of the orbiting wrap 1a.

[0021] The frame 5 is a member that supports the stationary scroll 2 and fixes the bearing of the crankshaft. The frame 5 is formed in a substantially rotationally symmetric shape and is fixed to the inner peripheral wall of the cylindrical chamber of the sealed container. The frame 5 is provided with an insertion hole through which the crankshaft is inserted.

[0022] The Oldham ring 11 is an annular member that receives the rotation of the crankshaft and orbits the orbiting scroll 1 without causing it to rotate on its own axis. The Oldham ring 11 is provided between the orbiting scroll 1 and the frame 5.

[0023] As the orbiting scroll 1 rotates due to the drive of the electric motor, the volume of the compression chambers 3 formed in succession decreases, and the gaseous refrigerant is compressed. The compressed gaseous refrigerant is discharged through the discharge port of the fixed scroll 2 into the upper space of the sealed container, and further flows into the space below the frame 5 through the gap between the frame 5 and the cylindrical chamber. Therefore, the upper space of the fixed scroll 2 and the lower space of the frame 5 are each filled with gaseous refrigerant substantially equal to the discharge pressure. The gaseous refrigerant that flows into the lower space of the frame 5 is discharged to the outside of the compressor 100 through the discharge pipe.

[0024] A back pressure chamber 6 is formed between the orbiting scroll 1 and the frame 5. The back pressure chamber 6 is filled with gaseous refrigerant at an intermediate pressure (the pressure between the suction pressure and the discharge pressure), which applies an upward force to the back surface 10 (bottom surface) of the orbiting scroll 1. This counteracts the thrust force caused by the compression pressure in the compression chamber 3, reducing leakage loss from the teeth of the orbiting wrap 1a and suppressing a decrease in compression efficiency. The pressure in the back pressure chamber 6 is determined by the position of the compression-side connecting passages 8a and 8b (see Figure 2), which will be described later. In Figure 1, the back pressure chamber 6 on the side of the orbiting scroll 1 and the back pressure chamber 6 on the bottom of the orbiting scroll 1 are depicted as not being connected, but in reality, they are connected by grooves or the like (not shown).

[0025] As shown in Figures 2 to 4, the orbiting scroll 1 is provided with a first compression-side communication passage 8a and a second compression-side communication passage 8b that intermittently connect the compression chamber 3 and the back pressure chamber 6. The dashed line in Figure 2 represents the orbiting scroll 1.

[0026] The first compression-side communication passage 8a intermittently connects the outer wire chamber 3a and the back pressure chamber 6 in the compression chamber 3, and the second compression-side communication passage 8b intermittently connects the inner wire chamber 3b and the back pressure chamber 6 in the compression chamber 3. This makes it possible to supply lubricating oil to both the outer wire chamber 3a and the inner wire chamber 3b. Figure 3 shows the state in which the outer wire chamber 3a (compression chamber 3) and the back pressure chamber 6 are connected via the first compression-side communication passage 8a, while Figures 2 and 4 show the state in which the outer wire chamber 3a (compression chamber 3) and the back pressure chamber 6 are not connected.

[0027] The first compression-side communication passage 8a is located closer to the periphery of the orbiting scroll 1 than the second compression-side communication passage 8b. The compression-side communication passages 8a and 8b are formed, for example, in a substantially U-shape in cross-section. The compression-side communication passages 8a and 8b have two openings on the upper surface of the orbiting scroll 1; one opening communicates with the compression chamber 3, and the other opening communicates with the fixed-side back pressure groove 9 provided on the lower surface of the fixed scroll 2.

[0028] The fixed-side back pressure groove 9 consists of an annular groove 9a provided on the peripheral edge of the fixed scroll 2 and an extension groove 9b extending from the annular groove 9a toward the center of the fixed scroll 2. The annular groove 9a and the extension groove 9b are in communication with the back pressure chamber 6. The openings on the other side of each compression-side communication passage 8a, 8b are intermittently in communication with the extension groove 9b, and their communication timings are different.

[0029] When the crank angle of the crankshaft is within the first compression-side communication range, the compression chamber 3 (outer wire chamber 3a) and the back pressure chamber 6 (fixed-side back pressure groove 9) are in communication via the first compression-side communication passage 8a (state shown in Figure 3). When the crank angle is within the second compression-side communication range, the compression chamber 3 (internal wire chamber 3b) and the back pressure chamber 6 (fixed-side back pressure groove 9) are in communication via the second compression-side communication passage 8b. The first compression-side communication range is, for example, the range of 120 to 240 degrees per revolution, and the second compression-side communication range is, for example, the range of 0 to 20 degrees and 270 to 360 degrees per revolution. During the rotation of the crankshaft, the first compression-side communication range does not overlap with the second compression-side communication range.

[0030] As shown in Figures 1 and 5, the fixed scroll 2 is provided with an intake-side communication passage 13 for intermittently connecting the intake chamber 12 and the back pressure chamber 6. The intake-side communication passage 13 intermittently communicates with a revolving-side back pressure groove 14 provided on the periphery of the upper surface of the revolving scroll 1. The revolving-side back pressure groove 14 communicates with the back pressure chamber 6. Figure 1 shows the state in which the intake chamber 12 and the back pressure chamber 6 are in communication via the intake-side communication passage 13, and Figure 5 shows the state in which the intake chamber 12 and the back pressure chamber 6 are not in communication.

[0031] The opening timing of the suction-side communication passage 13 differs from the opening timing of the compression-side communication passages 8a and 8b (see Figure 2). With this configuration, by making the opening timing of the suction-side communication passage 13 different from the opening timing of the compression-side communication passages 8a and 8b, it is possible to prevent communication between the compression chamber 3 and the suction chamber 12 via the back pressure chamber 6. This prevents gaseous refrigerant from flowing from the compression chamber 3 to the suction chamber 12 via the back pressure chamber 6, thereby suppressing a decrease in the compression efficiency of the compressor 100. In addition, it is possible to secure the oil supply differential pressure, which is the pressure difference between the discharge pressure and the pressure in the back pressure chamber 6, and to supply lubricating oil to the Oldham ring 11 and other components.

[0032] When the crank angle of the crankshaft is within the intake-side communication range, the intake chamber 12 and the back pressure chamber 6 communicate via the intake-side communication passage 13. The intake-side communication range is, for example, the range of 85 to 110 degrees within one rotation. The intake-side communication range is smaller than the compression-side communication range (the sum of the first compression-side communication range and the second compression-side communication range). In the rotation of the crankshaft, the intake-side communication range does not overlap with the first compression-side communication range and the second compression-side communication range. The intake-side communication range, the first compression-side communication range, and the second compression-side communication range are not limited to those described above and can be appropriately set within ranges where they do not overlap.

[0033] As shown in Figure 5, the compressor 100 is equipped with a valve body 16 that opens and closes the suction-side communication passage 13, and a spring 15 that biases the valve body 16 in the direction of opening. Preferably, the valve body 16 is positioned such that the pressure of the back pressure chamber 6 acts on one end (upper end) and the discharge pressure acts on the other end (lower end). With this configuration, when the discharge pressure is less than the back pressure, the gaseous refrigerant in the back pressure chamber 6 pushes up the valve body 16 at the timing of the suction-side communication passage 13 opening, causing the gaseous refrigerant in the back pressure chamber 6 to flow into the suction chamber 12, and the pressure in the back pressure chamber 6 decreases. When the pressure in the back pressure chamber 6 decreases to a predetermined value, the valve body 16 is pushed down by the discharge pressure, and the suction-side communication passage 13 is closed. This ensures a differential oil supply pressure, which is the pressure difference between the discharge pressure and the pressure in the back pressure chamber 6, and enables the supply of lubricating oil to the Oldham ring 11 and the like.

[0034] The valve body 16 and the spring 15 are provided in a valve chamber 22 that communicates with the suction chamber 12. The valve chamber 22 is formed in a cylindrical shape and is provided on the peripheral edge side of the fixed scroll 2 rather than the suction chamber 12. The valve body 16 is formed in a cylindrical shape having an outer diameter slightly smaller than the inner diameter of the valve chamber 22. The valve chamber 22 and the suction chamber 12 communicate with each other through a valve chamber communication passage 19 provided in the fixed scroll 2. The valve chamber communication passage 19 extends upward and obliquely toward the peripheral edge side (valve chamber 22 side) of the fixed scroll 2.

[0035] On the other end (lower end) side of the valve body 16, a reduced diameter portion 16b (which may also be a notch) is provided. The reduced diameter portion 16b is provided at a position that connects to the valve chamber communication passage 19 when the valve body 16 is in the closed state. This enables the valve body 16 to operate even when burrs or the like occur around the opening of the valve chamber communication passage 19.

[0036] The compressor 100 preferably includes a valve retainer 17 that restricts the movement of the valve body 16 in the direction of the other end (upward). The valve retainer 17 is formed, for example, in a cylindrical shape and has a through hole 17a through which the gaseous refrigerant discharged from the discharge port flows into the valve chamber 22. The spring 15 is, for example, a compression coil spring, and a fitting hole 22a for fitting the spring 15 is provided in the valve chamber 22. The fitting hole 22a communicates with the suction side communication passage 13.

[0037] In order to ensure the oil supply differential pressure, for example, when the oil supply differential pressure becomes less than 0.1 MPa, the valve body 16 opens, and when it becomes 0.1 MPa or more, the valve body 16 closes. The spring constant k of the spring 15, the cross-sectional area A1 of the valve chamber 22, the cross-sectional area A2 of the fitting hole 22a, and the cross-sectional area A3 of the through hole 17a are set. When the discharge pressure is Pd, the pressure in the back pressure chamber 6 is Pb, and the displacement of the spring 15 is x, the valve body 16 opens when Pd×A1<Pb×A2+kx is satisfied, and the back pressure chamber 6 and the suction chamber 12 are communicated. On the other hand, when Pd×A3>Pb×A1+kx is satisfied, the valve body 16 is closed, and the back pressure chamber 6 and the suction chamber 12 are non-communicated.

[0038] Preferably, the valve body 16 is provided with a sealing member 20 that separates the space where the back pressure chamber 6 pressure acts from the space where the discharge pressure acts. With such a configuration, leakage of gaseous refrigerant from the space where the discharge pressure acts to the space where the back pressure chamber 6 pressure acts can be prevented, and a decrease in compression efficiency can be suppressed. The sealing member 20 is, for example, an O-ring and is fitted into a groove 16a provided on the side surface of the valve body 16.

[0039] For example, under a pressure ratio of 1.5, the pressure in the back pressure chamber 6 is lower than the discharge pressure, thus ensuring a lubrication differential pressure. Under a pressure ratio of 1.3, the pressure in the back pressure chamber 6 may be higher than the discharge pressure, making it impossible to ensure a lubrication differential pressure. This could lead to poor lubrication of components such as the Oldham ring 11.

[0040] On the other hand, in this embodiment, at the timing of the suction-side communication passage 13 opening, the suction-side communication passage 13, located near the suction chamber 12 of the fixed scroll 2, communicates with the orbiting-side back pressure groove 14 of the orbiting scroll 1, and the gaseous refrigerant in the back pressure chamber 6 flows into the suction-side communication passage 13. The valve body 16 operates in response to the pressure of the gaseous refrigerant flowing into the suction-side communication passage 13 and moves to the valve retainer 17. The gaseous refrigerant in the back pressure chamber 6 then flows into the suction chamber 12 of the fixed scroll 2 through the valve chamber communication passage 19 with the suction chamber 12, and the pressure in the back pressure chamber 6 decreases. When the pressure in the back pressure chamber 6 decreases to a value that can secure the oil supply differential pressure, the valve body 16 is pushed by the action of the discharge pressure and closes the suction-side communication passage 13. Furthermore, at the timing when the suction-side communication passage 13 is connected, the compression-side communication passages 8a and 8b (see Figure 2) and the fixed-side back pressure groove 9 are not connected, thus preventing refrigerant from leaking from the compression chamber 3 to the suction chamber 12 via the back pressure chamber 6. As a result, it is possible to secure the oil supply differential pressure even under a pressure ratio of 1.3, enabling the supply of lubricating oil to the Oldham ring 11 and other components.

[0041] (modified version) In this embodiment, the orbiting scroll 1 is provided with a first compression-side communication passage 8a and a second compression-side communication passage 8b that intermittently connect the compression chamber 3 and the back pressure chamber 6, but is not limited to this. The orbiting scroll 1 may be provided with only one of the first compression-side communication passage 8a and the second compression-side communication passage 8b.

[0042] In this embodiment, the suction-side communication passage 13 is provided at a position where the suction-side communication range does not overlap with the first compression-side communication range and the second compression-side communication range, thereby differentiating the communication timing of the suction-side communication passage 13 from that of the compression-side communication passages 8a and 8b. However, the embodiment is not limited to this. For example, actuator-equipped valves may be provided in both the suction-side communication passage 13 and the compression-side communication passages 8a and 8b, and the opening and closing timings of each valve may be staggered to differentiate the communication timing of the suction-side communication passage 13 from that of the compression-side communication passages 8a and 8b.

[0043] Figure 6 shows a portion of the longitudinal cross-section of a scroll compressor 100 according to another embodiment. As shown in Figure 6, the fixed scroll 2 is provided with a stepped portion 21 at the end of the side wall on the outer circumference side of the intake chamber 12, and the valve chamber communication passage 19 may be in communication with the stepped portion 21. With this configuration, by providing the stepped portion 21, manufacturing becomes easier than when the valve chamber communication passage 19 is provided on the side wall of the intake chamber 12. This improves the productivity of the compressor 100. The stepped portion 21 is formed, for example, by counterboring.

[0044] Preferably, the through-hole 17a is provided with an enlarged diameter portion 17b that expands in diameter on the valve chamber 22 side. This increases the area over which the discharge pressure acts when the valve body 16 is open (when the valve body 16 is in contact with the valve retainer 17). This reduces the difference between the area over which the discharge pressure acts when the valve body 16 is open and the area over which the discharge pressure acts when the valve body 16 is closed.

[0045] [1] As described above, the scroll compressor 100 comprises a spiral scroll 1 having a spiral spiral wrap 1a, a fixed scroll 2 having a spiral fixed wrap 2a, a frame 5 supporting the fixed scroll 2, an intake chamber 12 for drawing in refrigerant, a compression chamber 3 formed between the spiral wrap 1a and the fixed wrap 2a for compressing the refrigerant, a back pressure chamber 6 formed between the spiral scroll 1 and the frame 5, compression-side communication passages 8a and 8b intermittently connecting the compression chamber 3 and the back pressure chamber 6, and an intake-side communication passage 13 for intermittently connecting the intake chamber 12 and the back pressure chamber 6, wherein the timing of the suction-side communication passage 13 is different from the timing of the compression-side communication passages 8a and 8b.

[0046] With this configuration, by making the opening timing of the suction-side communication passage 13 different from the opening timing of the compression-side communication passages 8a and 8b, it is possible to prevent communication between the compression chamber 3 and the suction chamber 12 via the back pressure chamber 6. This prevents refrigerant from flowing from the compression chamber 3 into the suction chamber 12 via the back pressure chamber 6, and suppresses a decrease in the compression efficiency of the compressor 100. As a result, it is possible to ensure lubrication of the Oldham ring 11 under low pressure ratio conditions.

[0047] [2] The scroll compressor 100 described in [1] above preferably comprises a valve body 16 that opens and closes the suction-side communication passage 13, and a spring 15 that biases the valve body 16 in the direction of opening, wherein the valve body 16 is positioned such that the pressure of the back pressure chamber 6 acts on one end and the discharge pressure acts on the other end.

[0048] With this configuration, at the timing of the opening of the suction-side communication passage 13, the gaseous refrigerant in the back pressure chamber 6 pushes up the valve body 16, causing the gaseous refrigerant in the back pressure chamber 6 to flow into the suction chamber 12, and the pressure in the back pressure chamber 6 to decrease. When the pressure in the back pressure chamber 6 drops to a predetermined value, the discharge pressure pushes down the valve body 16, closing the suction-side communication passage 13. This ensures a differential pressure for lubrication, which is the pressure difference between the discharge pressure and the pressure in the back pressure chamber 6, enabling the supply of lubricating oil to the Oldham ring 11 and other components.

[0049] [3] In the scroll compressor 100 described in [2] above, it is preferable that the valve body 16 is provided with a sealing member 20 that separates the space on which the pressure of the back pressure chamber 6 acts from the space on which the discharge pressure acts.

[0050] With this configuration, leakage of gaseous refrigerant from the space where the discharge pressure acts to the space where the pressure of the back pressure chamber 6 acts can be prevented, and a decrease in compression efficiency can be suppressed.

[0051] [4] In the scroll compressor 100 described in [2] or [3] above, the fixed scroll 2 may be configured to include a valve chamber 22 in which a valve body 16 is provided, a communication passage (valve chamber communication passage 19) that connects the valve chamber 22 and the intake chamber 12, and a stepped portion 21 provided at the end of the side wall on the outer circumference side of the intake chamber 12, wherein the communication passage (valve chamber communication passage 19) is in communication with the stepped portion 21.

[0052] With this configuration, by providing the stepped portion 21, manufacturing becomes easier than when the valve chamber communication passage 19 is provided in the side wall of the intake chamber 12. This improves the productivity of the compressor 100.

[0053] It should be noted that the scroll compressor is not limited to the configuration of the embodiment described above, nor is it limited to the effects and benefits described above. Furthermore, the scroll compressor can be modified in various ways without departing from the spirit of the present invention. For example, one or more of the various modifications described above may be arbitrarily selected and adopted in the configuration or method of the embodiment described above. [Explanation of Symbols]

[0054] 1...Swivel scroll, 1a...Swivel wrap, 1b...Swivel base plate, 2...Fixed scroll, 2a...Fixed wrap, 2b...Fixed base plate, 3...Compression chamber, 3a...Outer wire chamber, 3b...Inner wire chamber, 5...Frame, 6...Back pressure chamber, 8a...First compression side communication passage, 8b...Second compression side communication passage, 9...Fixed side back pressure groove, 9a...Annular groove, 9b...Extended groove, 10...Back surface, 11...Oldham ring, 12...Intake chamber, 13...Intake side communication passage, 14...Swivel side back pressure groove, 15...Spring, 16...Valve body, 16a...Concave groove, 16b...Reduced diameter section, 17...Valve retainer, 17a...Through hole, 17b...Expanded diameter section, 19...Valve chamber communication passage, 20...Sealing member, 21...Stepped section, 22...Valve chamber, 22a...Fitting hole, 100...Scroll compressor

Claims

1. A spiral scroll having a spiral wrap A fixed scroll having a spiral-shaped fixed wrap, A frame supporting the aforementioned fixed scroll, An intake chamber for drawing in refrigerant, A compression chamber formed between the swirling wrap and the fixed wrap, for compressing the refrigerant, A back pressure chamber formed between the orbiting scroll and the frame, A compression-side communication passage intermittently connects the compression chamber and the back pressure chamber, It comprises an intake-side communication passage for intermittently connecting the intake chamber and the back pressure chamber, A scroll compressor in which the timing of the suction-side communication passage is different from the timing of the compression-side communication passage.

2. The system comprises a valve body that opens and closes the intake side communication passage, and a spring that biases the valve body in the direction of opening. The scroll compressor according to claim 1, wherein the valve body is positioned such that the pressure of the back pressure chamber acts on one end and the discharge pressure acts on the other end.

3. The scroll compressor according to claim 2, wherein the valve body is provided with a sealing member that separates the space on which the pressure of the back pressure chamber acts from the space on which the discharge pressure acts.

4. The fixed scroll comprises a valve chamber in which the valve body is provided, a communication passage connecting the valve chamber and the intake chamber, and a stepped portion provided at the end of the side wall on the outer periphery side of the intake chamber. The scroll compressor according to claim 2 or 3, wherein the communication passage is in communication with the stepped portion.

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