Compressor and heat exchange system

Abstract

To provide a compressor which can inhibit deterioration of efficiency of the compressor, and to provide a heat exchange system.SOLUTION: A compressor 21 includes: a revolving scroll 40 having a revolving scroll lap 40a; a fixed scroll 41 in which the revolving scroll lap 40a is housed in a groove to form a compression chamber 48 for compressing a refrigerant; and an oil supply opening 56 which is provided at the radial outer side relative to a center of a bottom of the groove included in the fixed scroll 41 to supply oil to the compression chamber 48. The compression chamber 48 has: an outer line chamber at the outer line side of the revolving scroll lap 40a; and an inner line chamber at the inner line side. A maximum refrigerant enclosed volume formed by the revolving scroll 40 and the fixed scroll 41 is larger in the outer line chamber than in the inner line chamber. The oil supply opening 56 is provided at a position such that the oil supply opening 56 communicates with the outer line chamber before the refrigerant is enclosed in the outer line chamber and communicates with the inner line chamber after the refrigerant is enclosed in the inner line chamber.SELECTED DRAWING: Figure 3

Description

Technical Field

[0001] The present invention relates to a compressor and a heat exchange system.

Background Art

[0002] In heat exchange systems such as air conditioners and chillers, scroll compressors are used as compressors for circulating a refrigerant that exchanges heat with air, water, etc.

[0003] A scroll compressor forms a compression chamber by meshing a fixed scroll and an orbiting scroll. The compression chamber is formed on the outer circumference side and the inner circumference side of the orbiting scroll wrap. The one formed on the outer circumference side is the outer circumference chamber, and the one formed on the inner circumference side is the inner circumference chamber. In order to improve the sealing performance inside the outer circumference chamber and the inner circumference chamber, it is necessary to supply oil to each of the outer circumference chamber and the inner circumference chamber.

[0004] In a scroll compressor with an asymmetric tooth profile, the theoretical maximum volumes (maximum confinement volumes of the refrigerant) of the outer circumference chamber and the inner circumference chamber that make up the compression chamber are different, and in many cases, the volume of the outer circumference chamber is larger than the volume of the inner circumference chamber, and the seal length between the scroll wraps of the outer circumference chamber also increases. For this reason, if the same amount of oil is supplied to the outer circumference chamber and the inner circumference chamber, there is a risk that the oil on the outer circumference chamber side will be insufficient and the sealing performance will deteriorate.

[0005] Therefore, a scroll compressor is known in which the amount of oil supplied to the outer circumference chamber is made larger than the amount of oil supplied to the inner circumference chamber to improve the sealing performance (see, for example, Patent Document 1).

Prior Art Documents

Patent Documents

[0006]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0007] However, in the above conventional technology, when a large amount of high-temperature oil is supplied to the outer line chamber, there is a problem that the pressure in the outer line chamber rises, the power required for compression increases, and the compressor efficiency decreases.

Means for Solving the Problems

[0008] In view of the above problems, the present invention includes a swash scroll having a spiral curved portion (wrap, tooth), a fixed scroll having a spiral groove in which the swash scroll wrap is accommodated, and the swash scroll wrap is accommodated in the groove to form a compression chamber for compressing a refrigerant, an oil supply opening provided radially outside the center of the bottom of the groove (fixed scroll tooth bottom) of the fixed scroll for supplying oil to the compression chamber, and including, the compression chamber has an outer line chamber on the outer line side of the swash scroll wrap and an inner line chamber on the inner line side of the curved portion, and the maximum confinement volume of the refrigerant formed by the swash scroll and the fixed scroll is larger in the outer line chamber than in the inner line chamber. The oil supply opening is provided at a position that communicates with the outer line chamber before the refrigerant is confined in the outer line chamber and communicates with the inner line chamber after the refrigerant is confined in the inner line chamber. A compressor is provided.

Advantages of the Invention

[0009] According to the present invention, it is possible to provide a compressor and a heat exchange system that can suppress a decrease in compressor efficiency.

Brief Description of the Drawings

[0010]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Mode for Carrying Out the Invention

[0011] FIG. 1 is a diagram showing a configuration example of an air conditioner as an example of a heat exchange system. The heat exchange system circulates a refrigerant as a heat medium while compressing and expanding it in a sealed system, and indirectly contacts a fluid such as air or water that is the object of heat exchange to perform heat exchange between the refrigerant and the fluid. Therefore, the heat exchange system is not limited to an air conditioner as long as it is a system with such a configuration, and may be a refrigerator, a chiller, a heat pump water heater, or the like.

[0012] The air conditioner 10 includes an indoor unit 11 installed in a space (indoor) where air conditioning is performed and an outdoor unit 20 installed outdoors, circulates a refrigerant between the indoor unit 11 and the outdoor unit 20, and performs air conditioning by exchanging heat with the indoor air.

[0013] The indoor unit 11 and the outdoor unit 20 may each be composed of two or more units, and the indoor unit 11 may be connected to two or more units with respect to one outdoor unit 20. As the refrigerant, hydrofluorocarbon (HFC) or hydrofluoroolefin (HFO) can be used. Examples of HFC types include R410A and R32. Examples of HFO types include R1234yf.

[0014] The indoor unit 11 performs wireless communication using infrared rays or the like with a remote control, and receives various signals such as an operation command, a stop command, a command to change the set temperature, and a command to change the operation mode. The indoor unit 11 is connected to the outdoor unit 20 via a communication line and cooperates with the outdoor unit 20 to perform indoor air conditioning.

[0015] The indoor unit 11 receives an operation command from the remote control and starts up, and instructs the outdoor unit 20 to start up. After starting up, the outdoor unit 20 adjusts the rotation speed of the compressor, the opening degree of the expansion valve, etc., and controls the circulation amount of the refrigerant, etc., so that the indoor temperature becomes the set temperature.

[0016] The indoor unit 11 includes an indoor heat exchanger 12, an indoor fan 13, and an indoor fan motor 14. The indoor fan 13 is driven by the indoor fan motor 14, takes in indoor air, and sends it into the indoor heat exchanger 12. The indoor heat exchanger 12 has a heat transfer tube through which the refrigerant flows inside, and is configured such that the sent-in air contacts the surface of the heat transfer tube to perform heat exchange. The air heat-exchanged by the indoor heat exchanger 12 is discharged into the room.

[0017] In addition, the indoor unit 11 can be provided with various sensors for measuring the indoor temperature and the like, an expansion valve, and the like.

[0018] The outdoor unit 20 includes a compressor 21, an accumulator 22, a four-way valve 23, an expansion valve 24, an outdoor heat exchanger 25, an outdoor fan 26, and an outdoor fan motor 27. The compressor 21 is a scroll compressor, is driven by a compressor motor, compresses low-pressure gas refrigerant, and discharges it as high-pressure gas refrigerant. The accumulator 22 is a container for storing liquid return during transient periods, and adjusts the refrigerant to an appropriate dryness. The dryness is the ratio of the vapor occupying in the wet vapor indicating the mixed state of the vapor and the minute droplets.

[0019] The four-way valve 23 is a valve that switches the refrigerant flow path according to the operating state (operating mode) of the air conditioner 10. The operating modes include a cooling mode, a heating mode, a blowing mode, and the like. The expansion valve 24 is a valve that reduces the pressure of the high-pressure refrigerant and expands it. The outdoor fan 26 is driven by the outdoor fan motor 27, takes in outdoor air, and sends it into the outdoor heat exchanger 25. The outdoor heat exchanger 25, like the indoor heat exchanger 12, has a heat transfer tube through which the refrigerant flows inside, and is configured such that the sent-in air contacts the surface of the heat transfer tube to perform heat exchange. The air heat-exchanged by the outdoor heat exchanger 25 is discharged outdoors.

[0020] The outdoor unit 20 further includes a control device 28. The control device 28 is connected to the compressor 21, the four-way valve 23, the expansion valve 24, the indoor fan motor 14, and the outdoor fan motor 27, and controls these components. Specifically, it controls the rotation speed of the compressor motor, the opening degree of the expansion valve 24, the rotation speeds of the indoor fan motor 14 and the outdoor fan motor 27, etc. In order to control these, various sensors are also attached to the outdoor unit 20. The control device 28 performs these controls based on the information detected by the various sensors.

[0021] During the cooling operation, the indoor heat exchanger 12 is used as an evaporator, and the outdoor heat exchanger 25 is used as a condenser. Therefore, as shown by the arrows, the control device 28 circulates the refrigerant sealed in the system in the order of the compressor 21, the outdoor heat exchanger 25, the expansion valve 24, the indoor heat exchanger 12, the four-way valve 23, the accumulator 22, and the compressor 21.

[0022] The compressor 21 compresses the refrigerant in a low-temperature and low-pressure gaseous state (refrigerant gas) and discharges it as a high-temperature and high-pressure refrigerant gas. The outdoor heat exchanger 25 exchanges heat with the outdoor air and cools and condenses the refrigerant gas. The expansion valve 24 reduces the pressure of the refrigerant and vaporizes a part of it. For this reason, the refrigerant is supplied to the indoor unit 11 in a state where gas and liquid are mixed. The opening degree of the expansion valve 24 is adjusted by the control device 28 so as to have an appropriate amount of liquid.

[0023] The indoor heat exchanger 12 exchanges heat with the indoor air, completely vaporizes the condensed liquid refrigerant, and returns it to the outdoor unit 20 as refrigerant gas. The refrigerant gas returned from the indoor heat exchanger 12 is sent to the accumulator 22 through the four-way valve 23 and then returned to the compressor 21.

[0024] The control device 28 is mounted on the outdoor unit 20, but it is not limited to this. It may be mounted on the indoor unit 11 or on other central control panels, etc.

[0025] FIG. 2 is a cross-sectional view showing a configuration example of a scroll compressor as the compressor 21 used in the air conditioner 10. The compressor 21 shown in FIG. 2 is a vertical scroll compressor and includes a sealed container (chamber) 30, an electric motor (motor) 31, a compression mechanism 32, and a rotating shaft (crankshaft) 33 having an eccentric portion.

[0026] The chamber 30 is composed of a hollow cylindrical tube chamber 30a, a bottom chamber 30b welded to the lower part of the tube chamber 30a, and a lid chamber 30c welded to the upper part of the tube chamber 30a. The chamber 30 forms a sealed space inside when the upper and lower parts of the tube chamber 30a are closed by the bottom chamber 30b and the lid chamber 30c.

[0027] A suction pipe 34 connected to the suction port 46 of the compression mechanism 32 is welded or brazed to the lid chamber 30c. The discharge port 47 of the compression mechanism 32 communicates with the space inside the chamber 30, and a discharge pipe 35 that communicates the space inside the chamber 30 with the outside is welded or brazed to the side surface of the tube chamber 30a. In this way, the space inside the chamber 30 becomes a high-pressure atmosphere space where high-pressure refrigerant gas is discharged from the discharge port.

[0028] An oil storage portion 36 for storing oil is formed at the bottom of the chamber 30. The oil stored in the oil storage portion 36 is supplied to each sliding portion inside the compressor 21.

[0029] The motor 31 includes a stator 31a and a rotor 31b. The stator 31a is fixed to the chamber 30 by press-fitting, welding, or the like. The rotor 31b is rotatably disposed inside the stator 31a.

[0030] The crankshaft 33 includes a main shaft and an eccentric portion (pin portion) 33a. The upper side of the crankshaft 33 is rotatably supported by a main bearing 49 of a frame 42 provided in the compression mechanism 32, and the lower side is rotatably supported by a lower bearing 52 provided in a housing 51. The pin portion 33a rotates eccentrically with respect to the main shaft. The crankshaft 33 is provided with oil supply holes 37 such as vertical oil supply holes and horizontal oil supply holes for supplying the oil stored in the oil storage portion 36 to the main bearing 49, the lower bearing 52, etc. The vertical oil supply hole is provided so as to extend in the axial direction of the rotating shaft, which is the vertical direction in the case of a vertical scroll compressor, and the horizontal oil supply hole is provided so as to extend in a direction substantially perpendicular to the vertical oil supply hole. Note that the oil is supplied to each sliding portion through the oil supply hole 37 by an oil supply pump 53 into which a suction port is inserted in the oil storage portion 36. The oil supplied to each sliding portion circulates in the compressor 21 and is returned to the oil storage portion 36.

[0031] The compression mechanism 32 includes a orbiting scroll 40, a fixed scroll 41 that meshes with the orbiting scroll 40 to form a compression chamber 48 for compressing a refrigerant, a frame 42, an oldham ring 43, and a back pressure valve 44.

[0032] The orbiting scroll 40 has a spiral curved portion, that is, an orbiting scroll wrap having an involute as a cross-section line, an orbiting end plate, and an orbiting bearing 45 into which the pin portion 33a of the crankshaft 33 is inserted.

[0033] The fixed scroll 41 has a spiral curved portion, that is, a fixed scroll wrap having an involute as a cross-section line, and a fixed end plate. A suction port 46 is disposed at an outer peripheral portion of the fixed scroll wrap, and a discharge port 47 is disposed at a central portion of the fixed scroll wrap. Grooves exist on the outer line side and the inner line side of the fixed scroll wrap, and the grooves have a width in which the orbiting scroll wrap is accommodated and can perform an orbiting motion.

[0034] The orbiting scroll 40 is disposed so as to be orbitable relative to the fixed scroll 41, and a suction chamber communicating with the suction port 46 and a compression chamber 48 are formed by the orbiting scroll wrap and the fixed scroll wrap.

[0035] The frame 42 includes a main bearing 49 that rotatably supports the main shaft of the crankshaft 33. A fixed scroll 41 is fixed to a predetermined position on the frame 42 by bolts. A back pressure chamber 50 is formed between the orbiting scroll 40 and the frame 42.

[0036] The Oldham ring 43 has a key on the ring and is disposed between the orbiting scroll 40 and the frame 42. The key of the Oldham ring 43 is inserted into a keyway provided on the orbiting scroll 40 and a keyway provided on the frame 42, and causes the orbiting scroll 40 to perform a swinging motion without rotating itself.

[0037] The back pressure valve 44 is provided in a passage communicating the back pressure chamber 50 and the compression chamber 48, opens by a pressure difference, and controls the pressure (back pressure) of the back pressure chamber 50.

[0038] Therefore, the compression mechanism 32 is formed by meshing the orbiting scroll 40 and the fixed scroll 41, disposing the Oldham ring 43 between the orbiting scroll 40 and the frame 42, and screwing the fixed scroll 41 to the frame 42. On the upper surface side of the orbiting end plate, an inner compression chamber (inner wire chamber) on the inner wire side of the orbiting scroll 40 and an outer compression chamber (outer wire chamber) on the outer wire side of the orbiting scroll 40 are formed between the wraps of the orbiting scroll 40 and the fixed scroll 41. Also, a suction chamber is formed on the upper surface side of the orbiting end plate and on the suction side. Further, a back pressure chamber 50 is formed on the lower surface side of the orbiting end plate.

[0039] The motor 31 is supplied with power through a power supply terminal 55 provided in the cylinder chamber 30a.

[0040] FIG. 3 is a view of the inside of the compression mechanism 32 as seen from below. The compression mechanism 32 includes a swivel scroll 40 and a fixed scroll 41, and the fixed scroll 41 is fastened to the frame 42 so as to sandwich the swivel scroll 40. The fixed scroll 41 includes a fixed scroll wrap 41a having an involute as a cross-section line. The involute is a shape representing the locus taken by the tip of the thread when the thread is wound around a cylindrical body and then unwound, and is spiral. When viewed from the lower side in the axial direction of the main shaft, the portion of the fixed scroll wrap 41a of the fixed scroll 41 extends downward in a spiral shape, and grooves are formed on both the outer line side and the inner line side of the fixed scroll wrap 41a.

[0041] The swivel scroll 40 is inserted into the grooves formed on both the outer line side and the inner line side of the fixed scroll wrap 41a in such a manner that a swivel scroll wrap 40a extending upward in a spiral shape is accommodated therein. A compression chamber 48 is formed by the gap remaining after the swivel scroll wrap 40a is inserted into the grooves formed on both the outer line side and the inner line side of the fixed scroll wrap 41a.

[0042] The compression chamber 48 is composed of an inner line chamber formed on the inner line 40c side of the swivel scroll wrap 40a and an outer line chamber formed on the outer line 40b side of the swivel scroll wrap 40a.

[0043] The swivel scroll 40 is inserted into the eccentric pin portion 33a of the crankshaft 33 with a swivel bearing 45, and makes a swivel motion as the crankshaft 33 rotates. Due to the swivel motion of the swivel scroll 40, the volume of the compression chamber 48 is gradually reduced, compressing the refrigerant.

[0044] When viewed from the lower side in the axial direction of the main shaft, the fixed scroll 41 has a discharge port 47 at the center in the radial direction, and has a suction port 46 at the other end of a spiral groove formed along the fixed scroll wrap 41a with the discharge port 47 as one end. The suction port 46 is located at a position radially separated from the discharge port 47 and is provided on the side closer to the edge in the radial direction.

[0045] The compressor 21 is a compressor with an asymmetric tooth profile. The compression start angles of the inner line chamber and the outer line chamber are offset by approximately 180 degrees, and the theoretical maximum volume (the maximum confinement volume of the refrigerant) of the compression chamber 48 is larger in the outer line chamber than in the inner line chamber. The confinement volume is the volume of the space when it is closed by the orbiting scroll wrap 40a and the fixed scroll wrap 41a and is not in communication with either the suction port 46 or the discharge port 47.

[0046] The fixed scroll 41 is provided with an oil supply opening 56 for supplying oil to the compression chamber 48 radially outside the center of the tooth bottom (the portion where the upper surface of the orbiting scroll wrap 40a contacts). Since the oil supply opening 56 is arranged closer to the outer line chamber of the tooth bottom, the time for opening to the outer line chamber is longer than that to the inner line chamber, and more oil can be supplied to the outer line chamber than to the inner line chamber.

[0047] The compression chamber 48 is formed by the end plate of the orbiting scroll 40, the orbiting scroll wrap 40a, the end plate of the fixed scroll 41, and the fixed scroll wrap 41a, but there are minute gaps in its sliding portions. Since there is a pressure difference between adjacent compression chambers 48, a leakage flow occurs between adjacent compression chambers 48. Supplying oil to the compression chamber 48 seals this minute gap and has the effect of suppressing a decrease in compressor efficiency due to the leakage flow. In a compressor with an asymmetric tooth profile, since the maximum confinement volume is larger in the outer line chamber than in the inner line chamber, the sealing length of the gap in the sliding portion between the fixed scroll 41 and the orbiting scroll 40 is also longer in the outer line chamber, and the required oil supply amount to the outer line chamber is larger than that to the inner line chamber.

[0048] Since the oil supply opening 56 is provided radially outside the center of the tooth bottom of the fixed scroll wrap 41a, more oil can be supplied to the outer line chamber than to the inner line chamber, preventing the supply amount of oil to the outer line side from being insufficient and suppressing a decrease in sealing performance.

[0049] Note that FIG. 3 shows a back-pressure chamber side communication passage 57 and a mirror plate groove 58 that communicate from the back-pressure valve 44 to the back-pressure chamber 50. Oil is supplied into the compression chamber 48 from the oil supply opening 56 through the back-pressure chamber 50, the mirror plate groove 58, the back-pressure chamber side communication passage 57, the back-pressure valve 44, and the compression chamber side communication passage 59.

[0050] FIG. 4 is a diagram illustrating a refrigerant compression process associated with the turning motion of the turning scroll 40. FIG. 4(a) shows the compression process in the inner line chamber, and FIG. 4(b) shows the compression process in the outer line chamber. The turning scroll wrap 40a of the turning scroll 40 is formed in a spiral shape from one end (start of winding) near the central discharge port 47 to the other end (end of winding) near the suction port 46, and when the outer line side at the end of winding is in contact with the fixed scroll 41 (when the eccentric direction of the pin portion 33a of the crankshaft 33 is upward toward FIG. 4), it is assumed that the crank angle is at the 0° position.

[0051] When the refrigerant sucked in from the suction port 46 is at the position where the crank angle is 0°, the outer line side at the end of winding of the turning scroll wrap 40a is in contact with the inner line side of the fixed scroll 41, and the refrigerant is taken in only on the inner line side of the turning scroll wrap 40a. When the turning scroll 40 makes a turning motion and moves to the position where the crank angle is 180°, the inner line side at the end of winding comes into contact with the fixed scroll 41, a crescent-shaped inner line chamber 48a is formed, and the refrigerant is taken into the inner line chamber 48a.

[0052] When the turning scroll 40 advances to the position where the crank angle is 360° and returns to the crank angle of 0°, the volume of the crescent-shaped inner line chamber 48a decreases, and the refrigerant taken into the inner line chamber 48a is compressed. As the crank angle further advances and the refrigerant is compressed and communicates with the discharge port 47, the compression ends and the refrigerant is discharged from the discharge port 47. By repeating this, the compression of the refrigerant using the inner line chamber 48a is performed.

[0053] When the turning scroll 40 is at the position where the crank angle is 180°, the inner line 40c side at the end of winding of the turning scroll wrap 40a is in contact with the outer line side of the fixed scroll 41, and the refrigerant is taken in only on the outer line 40b side of the turning scroll wrap 40a to the outer line chamber 48b of the turning scroll wrap 40a. When the turning scroll 40 moves to the position where the crank angle is 360°, the outer line 40b side at the end of winding comes into contact with the fixed scroll 41, a crescent-shaped outer line chamber 48b is formed, and the refrigerant is taken into the outer line chamber 48b.

[0054] As the orbiting scroll 40 moves to the position of the crank angle of 360°, returns to the position of the crank angle of 0°, and advances to the positions of the crank angles of 180° and 360° again, the volume of the crescent-shaped outer line chamber 48b decreases, and the refrigerant taken into the outer line chamber 48b is compressed. As the crank angle advances, the compression chamber 48 gradually approaches the central discharge port 47, and when the outer line chamber 48b communicates with the discharge port 47, it is discharged from the discharge port 47. By repeating this, the compression of the refrigerant using the outer line chamber 48b is performed.

[0055] FIG. 5 is a cross-sectional view showing a configuration example near the back pressure valve 44 in the compressor 21. The fixed scroll 41 is fastened to the frame 42 so as to sandwich the orbiting scroll 40. A back pressure chamber 50 is formed between the orbiting scroll 40 and the frame 42, and the pressure (back pressure) in the back pressure chamber 50 is a pressure between the suction pressure and the discharge pressure.

[0056] The back pressure chamber 50 is connected by a compression chamber side communication passage 59 continuous with the oil supply opening 56, a back pressure chamber side communication passage 57, and a mirror plate groove 58. The back pressure valve 44 is provided between the compression chamber side communication passage 59 and the back pressure chamber side communication passage 57, and opens and closes by the differential pressure between the pressure in the compression chamber 48 where the oil supply opening 56 opens and the back pressure, and adjusts the back pressure. Here, a configuration including the mirror plate groove 58 is illustrated, but it is not limited thereto, and the mirror plate groove 58 may not be provided. In this case, the back pressure chamber 50 communicates with the back pressure chamber side communication passage 57 according to the rotational movement (crank angle) of the orbiting scroll 40.

[0057] By the way, since the inside of the chamber 30 is filled with the compressed high-temperature refrigerant, the oil stored in the oil storage portion 36 in contact with the refrigerant is at a high temperature. The oil is supplied to the main bearing 49, the lower bearing 52, between the swivel bearing 45 and the pin portion 33a, the back pressure chamber 50, etc. through the oil supply hole 37 formed inside the main shaft of the crankshaft 33.

[0058] The oil supplied to the back pressure chamber 50 lubricates the sliding parts between the O-ring 43 and the frame 42, between the O-ring 43 and the orbiting scroll 40, and between the orbiting scroll 40 and the fixed scroll 41. A part of the oil passes through the mirror plate groove 58, the back pressure chamber side communication passage 57, the back pressure valve 44, the compression chamber side communication passage 59, and the oil supply opening 56 in sequence and is supplied to the compression chamber 48. The oil supply opening 56 is provided radially outside the center of the tooth bottom of the fixed scroll 41, which is the outermost tooth bottom in the radial direction. The radial direction is the radial direction of the substantially circular fixed scroll 41 as viewed from the lower side in the axial direction of the main shaft. The tooth bottom of the fixed scroll 41 is a substantially flat portion that slides in contact with the upper surface of the orbiting scroll wrap 40a because the orbiting scroll wrap 40a extends upward.

[0059] In this way, by providing the oil supply opening 56 radially outside the center of the tooth bottom, the amount of oil supplied to the outer line chamber 48b with a maximum confinement volume larger than the inner line chamber 48a can be increased. As a result, the sealing performance can be enhanced and the compressor efficiency can be improved.

[0060] When high-temperature oil is supplied to the compression chamber 48, the refrigerant in the compression chamber 48 is heated by the high-temperature oil, and the pressure in the compression chamber 48 rises. When the pressure in the compression chamber 48 rises, the power of the compressor 21 increases and the compressor efficiency decreases. In particular, the inner line chamber 48a with a small maximum confinement volume has a large pressure increase and requires an appropriate amount of oil supply.

[0061] The amount of oil supplied to the inner line chamber 48a can be adjusted by changing the ratio of the time during which the oil supply opening 56 communicates with each of the inner line chamber 48a and the outer line chamber 48b. The ratio of this communication time can be adjusted by adjusting the radial position of the oil supply opening 56. In particular, the ratio of the communication time with the inner line chamber 48a, which is likely to have a large pressure increase due to high-temperature oil, can be reduced, and the ratio of the communication time with the outer line chamber 48b can be increased.

[0062] Specifically, the oil supply opening 56 can be provided at a position that communicates with the outer line chamber 48b before the refrigerant is confined therein and communicates with the inner line chamber 48a after the refrigerant is confined in the inner line chamber 48a.

[0063] If the amount of oil supplied to the inner line chamber 48a is reduced and the amount of oil supplied to the outer line chamber 48b is increased in order to suppress the pressure increase in the inner line chamber 48a, the pressure also increases in the outer line chamber 48b. By providing the oil supply opening 56 at a position where a part thereof communicates with the suction chamber before the refrigerant is confined in the outer line chamber 48b, the oil flows into the open space, so that the pressure rise in the outer line chamber 48b can be suppressed. Further, in the inner line chamber 48a where the appropriate amount of oil supply is achieved by adjusting the position of the oil supply opening 56, by providing the oil supply opening 56 at a position where it does not communicate with the suction chamber before the refrigerant is confined in the inner line chamber 48a, the oil does not flow before the confinement, so that the refrigerant in the suction chamber is not heated, and a decrease in the compressor efficiency due to the heating of the refrigerant can be suppressed.

[0064] FIG. 6 is a diagram for explaining the communication section between the compression chamber 48 and the back pressure chamber 50. The vertical axis represents the pressure ratio when the suction pressure is 1, and the horizontal axis represents the crank angle (°). The example shows the crank angle with 0° when the compression in the outer line chamber 48b starts. Since the compressor 21 has an asymmetric tooth profile, the position of the start of compression in the inner line chamber 48a is shifted by 180°.

[0065] When the position of the oil supply opening 56 is arranged radially outside the center of the tooth bottom of the fixed scroll 41, the communication section between the outer line chamber 48b and the back pressure chamber 50 becomes longer than the communication section between the inner line chamber 48a and the back pressure chamber 50.

[0066] When the position of the oil supply opening 56 is such that it communicates with the outer line chamber 48b before the refrigerant is confined in the outer line chamber 48b as described above and communicates with the inner line chamber 48a after the refrigerant is confined in the inner line chamber 48a, the communication between the outer line chamber 48b and the back pressure chamber 50 starts when the crank angle is smaller than 0°, and the communication between the inner line chamber 48a and the back pressure chamber 50 starts when the crank angle is larger than 180°.

[0067] In this way, by optimizing the amount of oil supplied to the compression chamber 48, it is possible to suppress the heating of the compression chamber 48 caused by the supply of high-temperature oil and improve the compressor efficiency.

[0068] FIG. 7 is a diagram showing an example of the range where the oil supply opening 56 is provided. FIG. 7 is a diagram showing only the fixed scroll 41 with the orbiting scroll 40 removed, and is a view seen from the lower side in the axial direction of the main shaft. The fixed scroll 41 includes a fixed scroll wrap 41a, and grooves 60 are provided on both sides adjacent to the fixed scroll wrap 41a. The grooves 60 are spiral, have a width and a depth in which the orbiting scroll wrap 40a is accommodated and can perform an orbiting motion.

[0069] The bottom of the groove 60 is substantially flat, one end (end of winding) is continuous with the suction port 46, and the other end (start of winding) is continuous with the discharge port 47. The oil supply opening 56 is a substantially circular opening and has a diameter smaller than the width of the orbiting scroll wrap 40a. This is because if the diameter of the oil supply opening 56 is larger than the width of the orbiting scroll wrap 40a, the inner line chamber 48a and the outer line chamber 48b will be connected through the oil supply opening 56, and the refrigerant will leak from the higher pressure side to the lower pressure side.

[0070] The position of the oil supply opening 56 is radially outside the boundary indicated by the dashed-dotted line A because the outer line chamber 48b communicates with the oil supply opening 56 before being confined. Also, the position of the oil supply opening 56 is radially outside the boundary indicated by the double-dashed-dotted line B because the inner line chamber 48a communicates with the oil supply opening 56 after being confined.

[0071] The position of the oil supply opening 56 is radially outside the boundary indicated by the dotted line C in order to supply more oil to the outer line chamber 48b than to the inner line chamber 48a. Also, the position of the oil supply opening 56 is radially inside the boundary indicated by the broken line D because it is necessary to communicate with the inner line chamber 48a.

[0072] Assuming that the direction in which the end of the revolving scroll wrap 40a contacts the fixed scroll 41 is at the position where the crank angle is 0°, the oil supply opening 56 can be provided at the bottom of the groove 60 continuous from the suction port 46 at positions where the crank angle is approximately 180° to approximately 325°.

[0073] From these facts, the oil supply opening 56 can be provided within the regions surrounded by the dash-dot line A, the two-dot chain line B, the dotted line C, and the dashed line D shown in FIG. 7. In order to increase the communication section between the outer line chamber 48b and the oil supply opening 56, it is moved closer to the outer side in the radial direction. In order to increase the communication section between the outer line chamber 48b and the oil supply opening 56 before the confinement, it is moved closer to the suction port 46 side.

[0074] Referring to FIG. 5 again, on the back pressure chamber side communication passage 57, a mirror plate groove 58 can be provided in the mirror plate that is butted against and connected to the frame 42 of the fixed scroll 41. Thereby, the back pressure chamber 50 can be put in a state of communicating with the back pressure chamber side communication passage 57 via the mirror plate groove 58. Then, the back pressure valve 44 can determine opening and closing only based on the pressure difference between the compression chamber 48 and the back pressure chamber 50, and can control the pressure of the back pressure chamber 50. Further, the back pressure valve 44 facilitates the control of the oil supply section between the inner line chamber 48a, the outer line chamber 48b, and the back pressure chamber 50.

[0075] For the refrigerant, the greater the adiabatic index, the greater the pressure rise when high-temperature oil is supplied to the compression chamber 48. In such a case, by adjusting the position of the oil supply opening 56 as described above, heating of the compression chamber 48 can be suppressed and a decrease in compressor efficiency can be suppressed. Examples of refrigerants with a large adiabatic index include difluoromethane (R32) and R410A containing 50% by mass each of R32 and pentafluoroethane (R125). For R32 and R410A, which have a large adiabatic index and a large pressure rise when high-temperature oil is supplied, such adjustment is effective. Note that the refrigerant is not limited to R32 and R410A, and is similarly effective for refrigerants having an adiabatic index of R410A or higher.

[0076] Although the embodiments of the compressor and the heat exchange system of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and can be modified within the scope that those skilled in the art can conceive, such as other embodiments, addition, modification, deletion, etc. As long as the functions and effects of the present invention can be achieved in any aspect, it is included in the scope of the present invention.

[0077] Therefore, according to the present invention, (1) a swash scroll having a spiral curve portion, a fixed scroll having a spiral groove for accommodating the curve portion, and forming a compression chamber for compressing a refrigerant by accommodating the curve portion in the groove, and an oil supply opening provided radially outside the center of the bottom of the groove of the fixed scroll for supplying oil to the compression chamber. The compression chamber has an outer chamber on the outer line side of the curve portion and an inner chamber on the inner line side of the curve portion. The maximum confinement volume of the refrigerant formed by the swash scroll and the fixed scroll is larger in the outer chamber than in the inner chamber. The oil supply opening is provided at a position that communicates with the outer chamber before the confinement of the refrigerant into the outer chamber and communicates with the inner chamber after the confinement of the refrigerant into the inner chamber, and a compressor can be provided.

[0078] According to the present invention, (2) the oil supply opening is provided in the outer groove of the inner and outer grooves in the radial direction of the fixed scroll, and the diameter of the oil supply opening is smaller than the width of the curve portion, and the compressor according to the above (1) can be provided.

[0079] According to the present invention, (3) a back pressure chamber to which the oil is supplied, and a back pressure valve provided between the oil supply opening and the back pressure chamber, and a communication passage communicating the back pressure chamber and the back pressure valve is always open, and the compressor according to the above (1) or (2) can be provided.

[0080] According to the present invention, (4) the refrigerant is a refrigerant having an adiabatic index of R410A or more, and the compressor according to any one of the above (1) to (3) can be provided.

[0081] According to the present invention, there is provided a system including the compressor according to any one of (1) to (4) above for compressing a refrigerant, and for effecting heat exchange with the refrigerant.

Explanation of Signs

[0082] 10…Air conditioner 11…Indoor unit 12…Indoor heat exchanger 13…Indoor fan 14…Indoor fan motor 20…Outdoor unit 21…Compressor 22…Accumulator 23…Four-way valve 24…Expansion valve 25…Outdoor heat exchanger 26…Outdoor fan 27…Outdoor fan motor 28…Control device 30…Chamber 30a…Cylindrical chamber 30b…Bottom chamber 30c…Cover chamber 31…Motor 31a…Stator 31b…Rotor 32…Compression mechanism 33…Crankshaft 33a…Pin portion 34…Suction pipe 35…Discharge pipe 36…Oil storage section 37…Oil supply hole 40…Swing scroll 40a…Swing scroll wrap 40b…Outer line 40c…Inner line 41…Fixed scroll 41a…Fixed scroll wrap 42…Frame 43…O-ring 44…Back pressure valve 45…Swing bearing 46…Suction port 47…Discharge port 48…Compression chamber 48a…Inner wire chamber 48b…Outer wire chamber 49…Main bearing 50…Back pressure chamber 51…Housing 52…Lower bearing 53…Oil supply pump 54…Lower frame 55…Power supply terminal 56…Oil supply opening 57…Back pressure chamber side connecting passage 58…Mirror plate groove 59…Compression chamber side connecting passage 60…Groove

Claims

1. A swash scroll having a spiral curve portion, a fixed scroll having a spiral groove in which the curve portion is accommodated, and forming a compression chamber for compressing a refrigerant by accommodating the curve portion in the groove, an oil supply opening provided radially outside the center of the bottom of the groove of the fixed scroll for supplying oil to the compression chamber and the compression chamber has an outer chamber on the outer line side of the curve portion and an inner chamber on the inner line side of the curve portion, and the maximum confinement volume of the refrigerant formed by the swash scroll and the fixed scroll is larger in the outer chamber than in the inner chamber, the oil supply opening is provided at a position that communicates with the outer chamber before the refrigerant is confined in the outer chamber and communicates with the inner chamber after the refrigerant is confined in the inner chamber, a compressor.

2. The compressor according to claim 1, wherein the oil supply opening is provided in the outer groove of the inner and outer grooves in the radial direction of the fixed scroll, and the diameter of the oil supply opening is smaller than the width of the curve portion.

3. a back pressure chamber to which the oil is supplied, a back pressure valve provided between the oil supply opening and the back pressure chamber and a communication passage communicating the back pressure chamber and the back pressure valve is always open, the compressor according to claim 1 or 2.

4. The compressor according to claim 1 or 2, wherein the refrigerant is a refrigerant having an adiabatic index of R410A or more.

5. A system including a compressor for compressing a refrigerant and exchanging heat with the refrigerant, wherein the compressor has a swash scroll having a spiral curve portion, a fixed scroll having a spiral groove in which the curve portion is accommodated, and forming a compression chamber for compressing the refrigerant by accommodating the curve portion in the groove, an oil supply opening provided radially outside the center of the bottom of the groove of the fixed scroll for supplying oil to the compression chamber and the compression chamber has an outer chamber on the outer line side of the curve portion and an inner chamber on the inner line side of the curve portion, and the maximum confinement volume of the refrigerant formed by the swash scroll and the fixed scroll is larger in the outer chamber than in the inner chamber, the oil supply opening is provided at a position that communicates with the outer chamber before the refrigerant is confined in the outer chamber and communicates with the inner chamber after the refrigerant is confined in the inner chamber, a heat exchange system.

Images