Compressor and air conditioner

Abstract

To provide a compressor and an air conditioner which can reduce liquid leakage, mechanical loss and abrasion.SOLUTION: In a compressor 21, a width of a first end face of a roller 38 facing a main bearing 34 is larger than a width of a second end face of the roller 38 facing an auxiliary bearing 35. Relationships of d1<d2, D2<D1 and d2-2e≤D2 are satisfied, where d1 represents an inner diameter on a main bearing 34 side of the roller 38; d2 represents an inner diameter on an auxiliary bearing 35 side of the roller 38; e is an amount of eccentricity indicating a distance from a center of a cross-section of a shaft 32 to a center of a cross-section of a pin part 31; D1 is a diameter of a first pressure range on a main bearing 34 side of a compression chamber 36; and D2 is a diameter of a second pressure range on an auxiliary bearing 35 side of the compression chamber 36.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present invention relates to a compressor and an air conditioner. [Background technology]

[0002] Some compressor discharge mechanisms compress the gas by closing a valve until the pressure in the compression chamber reaches the discharge pressure, and then open the valve when the pressure reaches the discharge pressure to discharge the compressed gas through the discharge port. In order to reduce the pressure loss when the compressed gas is discharged, it is necessary to enlarge the discharge port, but if the compressor is a rotary compressor, enlarging the discharge port will cause the outside and inside of the roller to communicate through the discharge port, which can cause refrigerant to leak from outside the compression chamber into the compression chamber.

[0003] Therefore, the end face width of the roller can be increased so that the outside and inside of the roller are not electrically connected through the discharge port. However, if the end face width of the roller is increased, the end face of the roller slides against the bearing, etc., increasing the sliding loss and reducing the amount of oil supplied from the end face of the roller to the compression chamber. Therefore, it is preferable not to increase the end face width of the roller more than necessary.

[0004] By locating the discharge port on the outside of the compression chamber, it is possible to suppress electrical conduction between the inside and outside of the roller without increasing the end face width of the roller. However, the portion of the discharge port that protrudes outside the compression chamber becomes large, and the flow path to the discharge port becomes narrow. In order to secure the flow path, the inner circumferential surface of the cylinder body can be recessed, but the recessed portion is an ineffective compression volume that is not involved in compression, and an increase in the recessed portion leads to an increase in the ineffective compression volume.

[0005] In view of these problems, a rotary compressor has been proposed in which the end face width of the roller is different between the discharge side of the compressed gas and the opposite side, the counter-discharge side, with the discharge side being larger than the counter-discharge side (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0006] [Patent Document 1] JP 2005-2832 A Summary of the Invention [Problem to be solved by the invention]

[0007] However, in the above conventional technology, the roller end face width is made larger on the discharge side than on the opposite side, which causes the roller to move toward the discharge side, widening the gap on the opposite side and increasing the leakage of fluid from the outside to the inside of the compression chamber. In addition, the roller is pressed toward the discharge side, which causes mechanical loss and wear on the roller end face. [Means for solving the problem]

[0008] In view of the above problems, the present invention provides a motor and A rotating shaft rotated by an electric motor and having an eccentric portion; a compression mechanism including first and second bearings for rotatably supporting a rotating shaft, a hollow cylinder into which the eccentric portion is inserted, and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, The width of the first end face of the cylinder facing the first bearing is larger than the width of the second end face of the cylinder facing the second bearing, and the inner diameter of the cylinder on the first bearing side is d 1 The inner diameter of the cylinder on the second bearing side is d 2 The eccentricity, which indicates the distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric part, is e, and the diameter of the first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid that has flowed into the first space formed by the first bearing, the cylindrical body, and the rotating shaft is D. 1 The diameter of the second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D 2 In this case, d 1 <d 2 , and D 2 <D 1 , and d 2-2e≦D 2 The compressor is characterized in that: Effect of the Invention

[0009] According to the present invention, fluid leakage, mechanical losses and wear can be reduced. [Brief description of the drawings]

[0010] [Figure 1] FIG. 1 is a diagram showing an example of the configuration of an air conditioning apparatus according to an embodiment of the present invention. [Diagram 2] FIG. 1 is a diagram showing an example of the configuration of a compressor used in an air conditioning apparatus. [Diagram 3] FIG. 2 is a diagram showing a first configuration example of a compression mechanism included in a compressor. [Figure 4] FIG. 4 is a diagram for explaining a discharge pressure range. [Diagram 5] 5A and 5B are diagrams illustrating pressure acting on an end face of a roller. [Figure 6] FIG. [Figure 7] FIG. 4 is a diagram showing a second configuration example of a compression mechanism included in the compressor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] 1 is a diagram showing an example of the configuration of an air conditioner according to this embodiment. The air conditioner 10 includes an indoor unit 11 installed in a space (indoors) where air conditioning is performed, and an outdoor unit 20 installed outdoors, and performs air conditioning by circulating a refrigerant as a fluid between the indoor unit 11 and the outdoor unit 20 and exchanging heat with the indoor air.

[0012] The indoor unit 11 and the outdoor unit 20 may each be configured with two or more units, and two or more indoor units 11 may be connected to one outdoor unit 20. As the refrigerant, hydrofluorocarbons (HFCs) and hydrofluoroolefins (HFOs) can be used. Examples of HFCs include R32 (CH 2 F 2 ), R410A(CH 2 F2 +C 2 HF 3 ) can be used, and R1234yf (CF 3 CF=CH 2 ) etc. can be used.

[0013] The indoor unit 11 includes an indoor heat exchanger 12, an indoor fan 13, and an indoor fan drive motor 14. The indoor fan 13 is driven by the indoor fan drive motor 14, takes in indoor air, and sends it to the indoor heat exchanger 12. The indoor heat exchanger 12 has a plurality of heat transfer tubes through which a refrigerant flows, and is configured so that the sent air comes into contact with the surfaces of the plurality of heat transfer tubes and exchanges heat with the refrigerant. The air that has undergone heat exchange by the indoor heat exchanger 12 is sent out into the room.

[0014] The indoor unit 11 can also include various sensors for measuring the indoor temperature, etc., and an indoor expansion valve that reduces the pressure of the refrigerant and expands it, and is capable of controlling the flow rate of the refrigerant.

[0015] The outdoor unit 20 includes a compressor 21, a four-way valve 22, an outdoor expansion valve 23, an outdoor heat exchanger 24, an outdoor fan 25, and an outdoor fan drive motor 26. The compressor 21 includes an accumulator 27 and is driven by a compressor drive motor to draw in low-pressure gas refrigerant from the accumulator 27, increase the pressure, and discharge it as high-pressure gas refrigerant. The accumulator 27 is a container for preventing liquid return to the compressor 21 during a transition and for separating the liquid, and adjusts the refrigerant to an appropriate dryness. The dryness is the proportion of steam in wet steam, which indicates the mixed state of steam and minute liquid droplets.

[0016] The four-way valve 22 is a valve that switches the direction of refrigerant flow depending on the operating state (operating mode) of the air conditioner 10. The operating modes are cooling mode, heating mode, ventilation mode, etc. The outdoor expansion valve 23 is a valve that reduces the pressure of high-pressure refrigerant and expands it, and is a valve that can control the flow rate of the refrigerant. The outdoor fan 25 is driven by an outdoor fan drive motor 26, takes in outdoor air, and sends it to the outdoor heat exchanger 24. Like the indoor heat exchanger 12, the outdoor heat exchanger 24 also has multiple heat transfer tubes through which the refrigerant flows, and is configured so that the sent-in air comes into contact with the surfaces of the multiple heat transfer tubes and exchanges heat with the refrigerant. The air that has been heat exchanged by the outdoor heat exchanger 24 is sent outside.

[0017] The outdoor unit 20 further includes a control device 28. The control device 28 is connected to the compressor 21, the four-way valve 22, the outdoor expansion valve 23, the indoor fan drive motor 14, and the outdoor fan drive motor 26, and controls these. The control device 28 controls the rotation speed of the compressor 21, the opening degree of the outdoor expansion valve 23, the rotation speed of the indoor fan drive motor 14, the rotation speed of the outdoor fan drive motor 26, etc. The control device 28 can perform these controls based on information detected by various sensors.

[0018] In the cooling mode, the indoor heat exchanger 12 is used as an evaporator, the outdoor heat exchanger 24 is used as a condenser, and the refrigerant sealed in the system is circulated in the order of the compressor 21, four-way valve 22, outdoor heat exchanger 24, outdoor expansion valve 23, indoor heat exchanger 12, four-way valve 22, accumulator 27, and compressor 21. In the heating mode, on the other hand, the indoor heat exchanger 12 is used as a condenser, and the outdoor heat exchanger 24 is used as an evaporator, and the refrigerant sealed in the system is circulated in the order of the compressor 21, four-way valve 22, indoor heat exchanger 12, outdoor expansion valve 23, outdoor heat exchanger 24, four-way valve 22, accumulator 27, and compressor 21.

[0019] Here, the air conditioner 10 has been taken as an example of a device equipped with a compressor 21, but the device is not limited to this and may be a refrigerator, a chiller unit, or the like.

[0020] 2 is a diagram showing an example configuration of the compressor 21 used in the air conditioner 10. The compressor 21 is a rotary compressor, and includes a motor 30 as an electric motor, a rotating shaft (shaft) 32 that is rotated by the motor 30 and has an eccentric portion (pin portion) 31, and a compression mechanism. The compressor 21 has the motor 30, shaft 32, and compression mechanism housed in a sealed container 33.

[0021] The compression mechanism includes a main bearing 34 as a first bearing that rotatably supports the shaft 32, and an auxiliary bearing 35 as a second bearing, and a cylinder 37 as a hollow cylindrical body that defines a compression chamber 36 together with the main bearing 34 and the auxiliary bearing 35 and compresses the fluid by means of a pin portion 31 that rotates within the compression chamber 36.

[0022] The motor 30 includes a hollow cylindrical stator 30a and a rotor 30b that is rotatably disposed within the stator 30a and has a permanent magnet as a magnet. The shaft 32 is disposed at the center of the rotor 30b when viewed from one side in the longitudinal direction (axial direction) of the shaft 32, and rotates with the rotation of the rotor 30b.

[0023] The container 33 is a hollow, sealed container that is circular in cross section and elongated in one direction, and the shaft 32 is disposed at the center of the cross section. The shaft 32 extends along the longitudinal direction of the container 33 to one side of the motor 30, and is connected to a compression mechanism disposed on one side of the motor 30.

[0024] The compression mechanism divides the compression chamber 36 into two spaces by a roller 38 as a hollow cylinder into which the pin portion 31 is inserted and a vane 39 as a plate-shaped partition plate, takes in a refrigerant as a fluid into one space within the compression chamber 36, and the roller 38 rotates eccentrically around the shaft 32 while in contact with the inner wall of the cylinder 37, thereby reducing the volume of that one space and compressing the refrigerant taken in that one space. An elastic member 40 such as a spring is provided at the end of the vane 39 so that the tip is always maintained in contact with the outer surface of the roller 38, and the vane 39 is always maintained in a state of being pressed against the roller 38.

[0025] The compression mechanism takes in refrigerant through a suction nozzle 41, and discharges the refrigerant compressed in the compression chamber 36 through a discharge valve into a space 42 between the motor 30 and the main bearing 34. The refrigerant is sent to a space 43 above the rotor 30b through a gap between the stator 30a and the rotor 30b that constitute the motor 30, and is discharged from a discharge nozzle 44 provided at the top of the container 33.

[0026] The motor 30 is disposed at approximately the center in the longitudinal direction of the container 33, and the compression mechanism is disposed on one side of the motor 30, for example, below the motor 30 when the container 33 is disposed with the discharge nozzle 44 facing upward. The compressor 21 may be a single-stage compressor in which the compression mechanism is composed of a main bearing 34, an auxiliary bearing 35, and one cylinder 37 and has only one compression chamber 36, or may be a multi-stage compressor in which the compression mechanism is composed of a main bearing 34, an auxiliary bearing 35, multiple cylinders 37, and partition plates sandwiched between the cylinders 37 and has multiple compression chambers 36.

[0027] For example, a two-stage compressor has two compression chambers, an upper compression chamber and a lower compression chamber, the upper compression chamber being formed by a main bearing, a cylinder, and a partition plate, and the lower compression chamber being formed by a sub-bearing, a cylinder, and a partition plate. Hereinafter, compressor 21 will be described as being vertically oriented with the longitudinal direction of container 33 oriented vertically, but compressor 21 may also be horizontally oriented with the longitudinal direction of container 33 oriented horizontally.

[0028] The discharge mechanism of a rotary compressor is mainly of the reed valve type. A reed valve is a valve in which one end of a thin, elastic plate is fixed and only the other end is open. The reed valve closes the discharge port provided in the main bearing 34 until the compression chamber 36 reaches the discharge pressure, at which point it is pushed up and opens the discharge port. The refrigerant compressed in the compression chamber 36 is discharged out of the compression chamber 36 through the open discharge port.

[0029] From the viewpoint of reducing pressure loss (discharge loss) when the refrigerant is discharged, it is desirable that the diameter of the discharge port is large in order to enlarge the flow path area. However, if the diameter of the discharge port is large, the outside and inside of the roller 38 will be conductive through the discharge port, which will cause refrigerant to leak from outside the compression chamber 36 to inside the compression chamber 36. For this reason, the discharge port is designed to be located at a position where the outside and inside of the roller 38 are not conductive, and to have a diameter that can be sealed with the end face of the roller 38.

[0030] In recent years, global warming has become a problem due to an increase in greenhouse gas emissions. Therefore, there is a demand for refrigerants with low global warming potential (GWP) to be used in air conditioners. To ensure the same cooling and heating capacity as conventionally used refrigerants such as R32 refrigerants, it is necessary to increase the circulation amount of low GWP refrigerants. Examples of low GWP refrigerants include R1234yt and R1234ze, which are mildly flammable refrigerants. The circulation amount can be increased by increasing the rotation speed of the compressor 21 or by increasing the displacement amount, which indicates the amount of refrigerant removed by the compressor 21 per unit time.

[0031] Increasing the rotation speed of the compressor 21 makes reliability difficult during high-speed operation, so increasing the displacement is effective. Increasing the displacement requires an increase in the diameter of the discharge port, but increasing the discharge diameter is not easy because it can cause refrigerant leakage from outside the compression chamber 36 to inside the compression chamber 36 due to electrical conduction between the outside and inside of the roller 38. Therefore, the discharge port can be located outside the compression chamber 36, but as mentioned above, the dead compression volume that is not involved in the compression of the refrigerant increases. Also, the end face width of the roller 38 can be increased, but this increases sliding loss and reduces the amount of lubricating oil.

[0032] As described in the above-mentioned conventional Patent Document 1, the end face width of roller 38 on the main bearing 34 side is made larger than the end face width of roller 38 on the sub-bearing 35 side, and only the end face width of roller 38 on the main bearing 34 side is made larger, thereby suppressing an increase in sliding loss.

[0033] However, by making the end face width of the roller 38 larger on the main bearing 34 side than on the sub-bearing 35 side, the roller 38 moves toward the main bearing 34 side, expanding the gap (clearance) between the roller 38 and the sub-bearing 35, and increasing the leakage of fluid from the outside to the inside of the compression chamber 36. In addition, the roller 38 moves toward the main bearing 34 side and is pressed against it, which increases mechanical loss such as sliding loss and wear on the end face of the roller 38.

[0034] In consideration of these problems, the end face width of roller 38 is made larger on the main bearing 34 side than on the sub-bearing 35 side to suppress electrical conduction between the outside and inside of roller 38 and to suppress movement of roller 38 toward the main bearing 34 side, thereby suppressing mechanical loss and increased wear on the end face of roller 38. Hereinafter, compressor 21 according to this embodiment will be described in detail with reference to the drawings.

[0035] Fig. 3 is a diagram showing an example of the configuration of a compression mechanism included in the compressor 21. Note that the configuration of the compressor 21 other than the compression mechanism is similar to that of the compressor 21 shown in Fig. 2. Fig. 3(a) is a diagram showing an example of the compression mechanism, and Fig. 3(b) is an enlarged view of a portion of the roller 38 in Fig. 3(a).

[0036] 3(a), the compression mechanism includes a main bearing 34 and an auxiliary bearing 35 that rotatably support a shaft 32 having a pin portion 31, a roller 38 into which the pin portion 31 is inserted, and a cylinder 37 that, together with the main bearing 34 and the auxiliary bearing 35, forms a compression chamber 36. The refrigerant is sucked through a suction nozzle 41, supplied to the compression chamber 36 through a suction port provided in the cylinder 37, and compressed in the compression chamber 36. After being compressed to a discharge pressure in the compression chamber 36, the refrigerant pushes up a reed valve, opens a discharge port provided in the main bearing 34, and is discharged from the discharge port to the outside of the compression chamber 36.

[0037] The pin portion 31 includes an upper pad 31a as a first support portion that faces the main bearing 34 and has a surface that slides on the main bearing 34, and a lower pad 31b as a second support portion that faces the secondary bearing 35 and has a surface that slides on the secondary bearing 35.

[0038] As shown in Fig. 3(b), grooves 50 are provided between the shaft 32 and the main bearing 34, between the main bearing 34 and the roller 38, and between the upper pad 31a of the pin portion 31 and the main bearing 34. As shown in Figs. 4(a) and 4(b), the grooves 50 are formed with a predetermined width around a hole 60 into which the shaft 32 is inserted.

[0039] Referring again to FIG. 3(b), grooves 51 are also provided between the shaft 32 and the sub-bearing , between the sub-bearing and the roller , and between the lower pad 31b of the pin portion 31 and the sub-bearing .

[0040] The inner corners of the roller 38 on the main bearing 34 side and the sub-bearing 35 side are cut at approximately 45° with respect to the axial direction of the shaft 32 and are chamfered.

[0041] The space between the groove 50 and the chamfered portion 52 formed by the main bearing 34, the roller 38, and the upper pad 31a of the pin portion 31 provided on the shaft 32, which is continuous with the groove 50, forms the discharge side space as the first space into which the discharged refrigerant flows.

[0042] The space between the groove 51 and the chamfered portion 52 formed by the auxiliary bearing 35, the roller 38, and the lower pad 31b of the pin portion 31 provided on the shaft 32, which is continuous with the groove 51, forms a counter-discharge side space as a second space into which the discharged refrigerant flows.

[0043] The refrigerant that has flowed into the discharge-side space applies pressure to the end surface 54 of the roller 38 located below the discharge-side space, the inclined surface of the roller 38 at the chamfered portion 52, and the discharge-side end surface of the compression chamber 36, which includes the sliding surface (upper thrust surface) 55 between the main bearing 34 of the upper pad 31a and the upper pad 31a. The range of the discharge-side end surface of the compression chamber 36 to which pressure is applied by the refrigerant is the discharge pressure range of the discharge-side end surface, which is the first pressure range.

[0044] The refrigerant that has flowed into the counter-discharge-side space applies pressure to end face 56 of roller 38 on the upper side of the counter-discharge-side space, the inclined surface of roller 38 at chamfered portion 52, a sliding surface (lower thrust surface) 57 between sub-bearing 35 of lower pad 31b and lower pad 31b, etc. The range of the counter-discharge-side end face of compression chamber 36 to which pressure is applied by the refrigerant is the discharge pressure range of the counter-discharge-side end face, which is the second pressure range.

[0045] Discharge port 58 is provided in main bearing 34, and cylinder 37 is provided with a notch 59 that is continuous with discharge port 58. In the example shown in Fig. 3(b), discharge port 58 and notch 59 are closed by end face 54 of roller 38 and the outer circumferential surface of roller 38 so that the refrigerant in compression chamber 36 is not discharged to the outside of compression chamber 36. Note that discharge port 58 may be provided in sub-bearing 35, but hereinafter, description will be given assuming that discharge port 58 is provided in main bearing 34.

[0046] The upper inner diameter d of the roller 38 1 is the inside diameter of the end face 54 of the roller 38. The end face 54 of the roller 38 is a ring shape with a circular outer shape and a circular hole in the center when viewed in a plan view in the axial direction of the shaft 32, i.e., when viewed from above, and d 1 is the diameter of the hole. The width of the end face 54 of the roller 38 is the radial width of the ring-shaped roller 38 when viewed from above in a plane, that is, the length obtained by subtracting the inner diameter from the outer diameter and dividing the result by 2.

[0047] The inner diameter d of the lower side of the roller 38 2 is the inside diameter of the end face 56 of the roller 38. The end face 56 of the roller 38 is a ring shape with a circular outer shape and a circular hole in the center when viewed in a plan view in the axial direction of the shaft 32, i.e., when viewed from below, and d 2 is the diameter of the hole. The width of the end face 56 of the roller 38 is the radial width of the ring-shaped roller 38 when viewed from below in a plane, that is, the length obtained by subtracting the inner diameter from the outer diameter and dividing the result by 2.

[0048] As shown in Fig. 3(b), the discharge side space is a space into which the refrigerant flows, and is configured from a groove 50 formed around the shaft 32, which has an L-shaped cross section cut in the axial direction of the shaft 32, and a chamfered portion 52 continuous with the groove 50. The discharge pressure range of the discharge side end face, in which the refrigerant that has flowed into the discharge side space exerts downward pressure, is a ring-shaped range when the groove 50 that constitutes the discharge side space is viewed from above, and the diameter of the discharge pressure range of the discharge side end face is the outer diameter D of the ring-shaped range. 1 It is.

[0049] As shown in Fig. 3(b), the opposite-discharge-side space is a space in which the refrigerant flows in, and is constituted by a groove 51 formed around the shaft 32 and having an L-shaped cross section cut in the axial direction of the shaft 32, and a chamfered portion 53 continuous with the groove 51. The discharge pressure range of the opposite-discharge-side end face, in which the refrigerant that has flowed into the opposite-discharge-side space exerts pressure upward, is a ring-shaped range when the groove 51 that constitutes the opposite-discharge-side space is viewed in plan, and the diameter of the discharge pressure range of the opposite-discharge-side end face is the outer diameter D of the ring-shaped range. 2 It is.

[0050] The shaft 32 has different outer diameters at the upper and lower sides across the pin portion 31, with the upper outer diameter being larger than the lower outer diameter. The rotor 30b is attached to the upper side of the shaft 32, and a certain outer diameter is required to support the rotor 30b, but since there is nothing to support the lower side, the outer diameter may be smaller than the upper side.

[0051] By making the width of the upper end face 54 of the roller 38 larger than the width of the lower end face 56 of the roller 38, the discharge port can be closed by the upper end face 54, and communication between the discharge port and the inside of the roller 38 can be suppressed. Making the width of the upper end face 54 of the roller 38 larger than the width of the lower end face 56 of the roller 38 is possible because the outer diameters of the end faces 54 and 56 of the roller 38 are the same, and therefore, d 1 <d 2 This means that the following holds true.

[0052] The area of ​​the lower chamfered portion 53 of the roller 38 in a plan view is larger than the area of ​​the upper chamfered portion 52 of the roller 38 in a plan view. Therefore, the pressure applied to the roller 38 from below is larger than the pressure applied to the roller 38 from above. Then, the roller 38 is lifted upward and pressed against the main bearing 34, and the clearance between the roller 38 and the sub-bearing 35 increases. The increase in the clearance increases leakage loss and mechanical loss and wear caused by the pressing of the upper end face 54 of the roller 38.

[0053] The refrigerant discharged from the compression chamber 36 also flows into the discharge space and the opposite discharge space. The refrigerant in the discharge space applies pressure in the axial direction of the shaft 32, i.e., downward. Meanwhile, the refrigerant in the opposite discharge space applies pressure in the axial direction of the shaft 32, i.e., upward. The pressure increases as the area of ​​the range to which pressure is applied increases.

[0054] Since upper end face 54 of roller 38 is pressed against main bearing 34 and the clearance between roller 38 and sub-bearing 35 is expanding, it is believed that if pressure could be applied to roller 38 in a downward direction, the problems of upper end face 54 of roller 38 being pressed against roller 38 and the expanding clearance could be solved.

[0055] Therefore, the pressure applied downward to end face 54 of roller 38 is made greater than the pressure applied upward to end face 56 of roller 38. This means that the pressure applied to the area where the upper end face 54 of roller 38 and the discharge pressure range of the discharge side end face overlap is greater than the pressure applied to the area where the lower end face 56 of roller 38 and the discharge pressure range of the anti-discharge side end face overlap.

[0056] The area of ​​the chamfered portions 52, 53 of the roller 38 in a plan view is larger on the lower side than on the upper side of the roller 38, and if the lower end face 56 of the roller 38 overlaps with the discharge pressure range of the opposite-discharge-side end face, then the upper end face 54 of the roller 38 should also overlap with the discharge pressure range of the discharge-side end face. The overlap of the lower end face 56 of the roller 38 with the discharge pressure range of the opposite-discharge-side end face means that the distance from the center of the cross section of the shaft 32 to the left edge of the discharge pressure range of the opposite-discharge-side end face as viewed from the front is equal to or greater than the distance to the lower end face 56 of the roller 38, as shown in FIG. 3(b).

[0057] The distance from the center of the cross section of the shaft 32 to the edge of the discharge pressure range of the opposite discharge side end surface is half the diameter of the discharge pressure range of the opposite discharge side end surface, D 2 The distance from the center of the cross section of the shaft 32 to the lower end face 56 of the roller 38 is d 2 Since the center of the cross section of the roller 38 is offset from the center of the cross section of the shaft 32 by an eccentricity e, d 2 Therefore, the lower end surface 56 of the roller 38 overlaps with the discharge pressure range of the opposite end surface of the roller 38, and the 2 / 2-e≦D 2 This means that / 2 holds true, and by rearranging, we get d 2 -2e≦D 2 It becomes.

[0058] In order to make the pressure applied to the overlapping area of ​​the upper end face 54 of the roller 38 and the discharge pressure range of the discharge side end face greater than the pressure applied to the overlapping area of ​​the lower end face 56 of the roller 38 and the discharge pressure range of the opposite discharge side end face, the discharge pressure range of the discharge side end face should be made greater than the discharge pressure range of the opposite discharge side end face. 2 <D 1 This means that the following holds true.

[0059] In summary, d 1 <d 2 , and d 2 -2e≦D 2 , and D2 <D 1 By providing a compressor in which the above relationship is satisfied, even if the discharge port provided in the main bearing 34 is increased in diameter, the width of the end face 54 of the roller 38 on the main bearing 34 side can be increased to suppress conduction between the outside and inside of the roller 38, and the pressing of the roller 38 against the main bearing 34 can be reduced and deviations in the clearance of the roller 38 can be suppressed, thereby improving compressor efficiency and reliability against roller end face sliding.

[0060] Fig. 5 is a diagram for explaining the condition for balancing the load due to the pressure on the upper side of roller 38 and the load due to the pressure on the lower side of roller 38. Fig. 5(a) is a diagram viewed from above with main bearing 34 removed, and Fig. 5(b) is a diagram viewed from below with sub-bearing 35 removed.

[0061] In order to prevent the clearance above and below the roller 38 from becoming uneven, it is necessary that the load due to the pressure on the upper side of the roller 38 and the load due to the pressure on the lower side of the roller 38 are balanced.

[0062] In order for the load due to pressure on the upper side of roller 38 and the load due to pressure on the lower side of roller 38 to be balanced, when viewed in a plane in the axial direction of shaft 32, the area of ​​the upper side of roller 38 where the load is applied and the area of ​​the lower side of roller 38 where the load is applied need to be approximately identical.

[0063] The area of ​​the upper side of the roller 38 on which the load is applied is the sum of the area of ​​a flat portion 70 of the chamfered portion 52 of the roller 38 as viewed from above, and the area of ​​a portion 71 where the end face 54 of the roller 38 and the discharge pressure range of the discharge side end face overlap. Here, this area is represented as A 1 The flat portion 70 is a ring-shaped portion of a substantially constant width located immediately inside the upper end face 54 of the roller 38 when viewed from above in Fig. 5(a). The portion 71 where the discharge pressure ranges of the discharge side end faces overlap is on the end face 54 of the roller 38 and is a portion extending from the inside to the outside of the end face 54 of the roller 38.

[0064] The area of ​​the lower side of the roller 38 on which the load is applied is the sum of the area of ​​a flat portion 72 of the lower chamfered portion 53 of the roller 38 as viewed from below, and the area of ​​a portion 73 where the end face 56 of the roller 38 and the discharge pressure range of the end face on the opposite discharge side overlap. Here, this area is represented as A 2 The flat portion 72 is a ring-shaped portion of a substantially constant width located immediately inside the lower end face 56 of the roller 38 when viewed from below in Fig. 5(b). The portion 73 where the discharge pressure ranges of the opposite discharge side end faces overlap is on the end face 56 of the roller 38 and is a portion extending from the inside to the outside of the end face 56 of the roller 38.

[0065] In order to balance the loads on the top and bottom of the roller 38, A 1 and A 2 are substantially the same.

[0066] This makes the clearance above and below the roller 38 uniform, reducing leakage loss and suppressing mechanical loss and wear caused by the roller 38 being pressed against the main bearing 34.

[0067] A resultant force of pressure above and below roller 38 acts downward on roller 38. When compressor 21 is started, the refrigerant is not compressed, so no force due to pressure is generated downward due to only the weight of roller 38. After compressor 21 is started, the refrigerant is compressed, and roller 38 is constantly subjected to a load due to pressure.

[0068] Then, in order to balance the loads on the top and bottom of the roller 38, A 1 and A 2 are kept substantially the same, when the compressor 21 is started, the clearance below the rollers 38 is small due to their own weight, and the rollers 38 are in a lowered state, but after the compressor is started, the clearances above and below the rollers 38 are equalized, so that the rollers 38 are lifted up compared to when the compressor is started. This causes the rollers 38 to move up and down.

[0069] The above-mentioned vertical movement of roller 38 can be suppressed by configuring roller 38 so that it always receives a load downward from the time compressor 21 is started up to the time of operation after startup. If the vertical movement of roller 38 is suppressed and roller 38 is always in a lowered state, roller 38 will not be strongly pressed against main bearing 34 or sub bearing 35 due to the vertical movement of roller 38, and mechanical loss and wear due to the pressing of end faces 54, 56 of roller 38 can be suppressed.

[0070] The area of ​​the upper side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 70 of the chamfered portion 52 on the upper side of the roller 38 as viewed from above, and the area of ​​the portion 71 where the end face 54 of the roller 38 and the discharge pressure range of the discharge side end face overlap. Here, this area is expressed as A 3 Let us assume that.

[0071] The area of ​​the lower side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 72 of the lower chamfered portion 53 of the roller 38 as viewed from below, and the area of ​​the portion 73 where the end face 56 of the roller 38 and the discharge pressure range of the end face opposite the discharge side overlap. Here, this area is expressed as A 4 Let us assume that.

[0072] In order to configure the roller 38 so that it always receives a load downward from the time the compressor 21 is started up to the time of operation after the start-up, the upper area A of the roller 38 on which the load is applied must be 3 The area A of the lower part of the roller 38 on which the load is applied is 4 The larger the better, A 4 3 This means that the following holds true.

[0073] 6 is a diagram illustrating the thrust surface. The thrust surface is a surface that receives a force acting in the axial direction of the shaft 32, and includes a sliding surface (upper thrust surface) 55 when the upper pad 31a of the pin portion 31 slides on the main bearing 34, and a sliding surface (lower thrust surface) 57 when the lower pad 31b of the pin portion 31 slides on the sub-bearing 35.

[0074] ​If the discharge pressure range of the discharge side end face is larger than the upper thrust surface 55, the upper pad 31a will get into the groove 50, and will not be able to withstand the force acting in the axial direction of the shaft 32, and the thrust will not function effectively. Similarly, if the discharge pressure range of the opposite discharge side end face is larger than the lower thrust surface 57, the lower pad 31b will get into the groove 51, and the thrust will not function effectively.

[0075] Here, as shown in FIG. 6, the diameter of the discharge pressure range of the discharge side end face of the compression chamber 36 is D 1 The diameter of the discharge pressure range of the end surface of the compression chamber 36 opposite the discharge side is D 2 The distance (maximum dimension) from the center of the cross section of the shaft 32 to the most distant edge of the pin portion 31 sliding on the main bearing 34, i.e., the upper pad 31a, is defined as L 1 The distance (maximum dimension) from the center of the cross section of the shaft 32 to the most distant edge of the pin portion 31 sliding on the sub-bearing 35, i.e., the lower pad 31b, is defined as L 2 Let us assume that.

[0076] In order for the upper and lower thrusts to function effectively, it is sufficient that the upper thrust surface 55 is larger than the discharge pressure range of the discharge side end face, and the lower thrust surface 57 is larger than the discharge pressure range of the opposite discharge side end face. This means that the maximum diameter of the upper thrust surface 55 is larger than the diameter of the discharge pressure range of the discharge side end face, and D 1 <2×L. This also means that the maximum diameter of the lower thrust surface 57 is greater than the diameter of the discharge pressure range of the opposite discharge side end surface, and D 2 <2×L2 holds.

[0077] In this way, by making the upper and lower thrusts function effectively, the stability of the operation of the compressor 21 can be improved.

[0078] In the examples so far, as shown in Fig. 3(b), a case has been described in which the end face 56 of the roller 38 overlaps with the discharge pressure range of the end face on the opposite side of the compression chamber 36. As shown in Fig. 7(a), the groove 51 may not extend to the lower end face 56 of the roller 38. In this case, the end face 56 of the roller 38 does not overlap with the discharge pressure range of the end face on the opposite side of the compression chamber 36.

[0079] Referring to FIG. 7(a), the inner diameter d of the upper side of the roller 38 is 1 is the inside diameter of the end face 54 of the roller 38 facing the main bearing 34. The inside diameter d 2 is the inner diameter of the end face 56 of the roller 38 facing the auxiliary bearing 35. The discharge pressure range of the discharge side end face of the compression chamber 36 is a ring-shaped range when the groove 50 constituting the discharge side space is viewed in plan, and the diameter is the outer diameter D of the ring-shaped range. 1 The discharge pressure range of the end surface of the compression chamber 36 on the opposite side to the discharge side is a ring-shaped range when the groove 51 constituting the opposite side space is viewed in plan, and the diameter of the ring-shaped range is the outer diameter D 2 It is.

[0080] Even if the end face 56 of the roller 38 does not overlap the discharge pressure range of the end face on the opposite side of the compression chamber 36, by making the width of the end face 54 of the roller 38 larger than the width of the end face 56 of the roller 38, the discharge port can be closed by the upper end face 54, and communication between the discharge port and the inside of the roller 38 can be suppressed. Making the width of the end face 54 of the roller 38 larger than the width of the end face 56 of the roller 38 is possible because the outer diameters of the end faces 54 and 56 of the roller 38 are the same. 1 <d 2 This means that the following holds true.

[0081] The area of ​​flat surface portion 72 of lower chamfered portion 53 of roller 38 viewed from below in a plan view is greater than the area of ​​flat surface portion 70 of upper chamfered portion 52 of roller 38 viewed from above in a plan view. Therefore, the pressure applied to roller 38 from below is greater than the pressure applied to roller 38 from above, and roller 38 is pressed against main bearing 34, and the clearance between roller 38 and sub-bearing 35 increases.

[0082] To prevent this clearance from widening, it is necessary to apply pressure to the end face 54 of the roller 38, and the condition is that the end face 54 of the roller 38 overlaps with the discharge pressure range of the discharge side end face of the compression chamber 36 so that pressure can be applied from above. In this case, the end face 56 of the roller 38 does not overlap with the discharge pressure range of the opposite discharge side end face of the compression chamber 36.

[0083] The distance from the center of the cross section of the shaft 32 to the edge of the discharge pressure range of the discharge side end face of the compression chamber 36 is half the diameter of the discharge pressure range of the discharge side end face of the compression chamber 36, D 1 The distance from the center of the cross section of the shaft 32 to the end face 54 of the roller 38 is d 1 Since the center of the cross section of the roller 38 is offset from the center of the cross section of the shaft 32 by an eccentricity e, d 1 Therefore, the end surface 54 of the roller 38 overlaps with the discharge pressure range of the discharge side end surface of the compression chamber 36 only when the discharge pressure range is d 1 / 2-e≦D 1 This means that / 2 holds true, and by rearranging, we get d 1 -2e≦D 1 It becomes.

[0084] The distance from the center of the cross section of the shaft 32 to the edge of the discharge pressure range of the opposite discharge end surface of the compression chamber 36 is half the diameter of the discharge pressure range of the opposite discharge end surface of the compression chamber 36, D 2 The distance from the center of the cross section of the shaft 32 to the end face 56 of the roller 38 is d 2 Since the center of the cross section of the roller 38 is offset from the center of the cross section of the shaft 32 by an eccentricity e, d 2Therefore, the end surface 56 of the roller 38 does not overlap with the discharge pressure range of the end surface of the compression chamber 36 on the opposite side to the discharge side, and 2 / 2-e>D 2 This means that / 2 holds true, and by rearranging, we get D 2 <d 2 The result is -2e.

[0085] In order to make the pressure applied to the discharge pressure range of the discharge side end face of the compression chamber 36 larger than the pressure applied to the discharge pressure range of the opposite discharge side end face of the compression chamber 36, the area of ​​the discharge pressure range of the upper end face should be made larger than the area of ​​the discharge pressure range of the opposite discharge side end face. 2 <D 1 This means that the following holds true.

[0086] If the end face 56 of the roller 38 does not overlap with the discharge pressure range of the opposite discharge side end face, the refrigerant flowing into the chamfered portion 53 will apply axial pressure to both the roller 38 and the auxiliary bearing 35 of the shaft 32.

[0087] Then, simply do the above d 1 <d 2 , and d 1 -2e≦D 1 , and D 2 <d 2 -2e and D 2 <D 1 However, simply providing a compressor in which the above condition holds may not result in uniform clearances above and below the rollers 38.

[0088] In order to equalize the clearance above and below the roller 38, it is necessary that the forces due to the pressure above and below the roller 38 are balanced.

[0089] In order for the load due to pressure on the upper side of roller 38 and the load due to pressure on the lower side of roller 38 to be balanced, when viewed in a plane in the axial direction of shaft 32, the area of ​​the upper side of roller 38 where the load is applied and the area of ​​the lower side of roller 38 where the load is applied need to be approximately identical.

[0090] The area of ​​the upper side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 70 of the chamfered portion 52 on the upper side of the roller 38 as viewed from above, and the area of ​​the portion 71 where the end face 54 of the roller 38 and the discharge pressure range of the discharge side end face overlap. Here, this area is expressed as A 5 Let us assume that.

[0091] The area of ​​the lower side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 72 of the chamfered portion 53 on the lower side of the roller 38 as viewed from below, and the area of ​​the portion where the end face 56 of the roller 38 and the discharge pressure range of the end face on the opposite side of the discharge side overlap. Here, this area is expressed as A 6 In addition, since the discharge pressure range of the end face 56 of the roller 38 and the end face on the opposite side to the discharge side do not overlap, the area of ​​this portion is zero.

[0092] In order to balance the loads on the top and bottom of the roller 38, A 5 and A 6 are substantially the same.

[0093] Even in this case, a resultant force of the pressure above and below roller 38 acts downward on roller 38. When compressor 21 is started, the refrigerant is not compressed, so no force due to pressure is generated downward due to only the weight of roller 38. After compressor 21 is started, the refrigerant is compressed, and roller 38 is constantly subjected to a load due to pressure. Therefore, roller 38 moves up and down.

[0094] The above-mentioned vertical movement of roller 38 can be suppressed by configuring roller 38 so that it always receives a load downward from the time compressor 21 is started up to the time of operation after startup. If the vertical movement of roller 38 is suppressed and roller 38 is always in a lowered state, roller 38 will not be strongly pressed against main bearing 34 or sub bearing 35 due to the vertical movement of roller 38, and mechanical loss and wear due to the pressing of end faces 54, 56 of roller 38 can be suppressed.

[0095] The area of ​​the upper side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 70 of the chamfered portion 52 on the upper side of the roller 38 as viewed from above, and the area of ​​the portion 71 where the end face 54 of the roller 38 and the discharge pressure range of the discharge side end face overlap. Here, this area is expressed as A 7 Let us assume that.

[0096] The area of ​​the lower side of the roller 38 on which the load is applied is the sum of the area of ​​the flat portion 72 of the chamfered portion 53 of the lower roller 38 when viewed from below the roller 38, and the area of ​​the portion 73 where the end face 56 of the roller 38 and the discharge pressure range of the end face on the opposite side of the discharge side overlap. Here, this area is expressed as A 8 Let us assume that.

[0097] In order to configure the roller 38 so that it always receives a load downward from the time the compressor 21 is started up until the time the compressor 21 is in operation after the start-up, the area A on which the load is applied to the upper side of the roller 38 is 7 The area A on which the load is applied to the lower side of the roller 38 is 8 The larger the better, A 8 7 This means that the following holds true.

[0098] Also in this case, if the discharge pressure range of the discharge side end face of the compression chamber 36 is larger than the upper thrust surface 55, the upper pad 31a will get into the groove 50, and will not be able to withstand the force acting in the axial direction of the shaft 32, and the thrust will not function effectively. Similarly, if the discharge pressure range of the anti-discharge side end face of the compression chamber 36 is larger than the lower thrust surface 57, the lower pad 31b will get into the groove 51, and the thrust will not function effectively.

[0099] In order for the upper and lower thrusts to function effectively, it is sufficient that the upper thrust surface 55 is larger than the discharge pressure range of the discharge side end face of the compression chamber 36, and the lower thrust surface 57 is larger than the discharge pressure range of the opposite discharge side end face of the compression chamber 36. This means that the maximum diameter of the upper thrust surface 55 is larger than the diameter of the discharge pressure range of the discharge side end face of the compression chamber 36, and D 1 ​<2×L. This also means that the maximum diameter of the lower thrust surface 57 is greater than the diameter of the discharge pressure range of the end surface of the compression chamber 36 on the opposite side to the discharge side, D 2 <2×L2 holds.

[0100] In this way, by making the upper and lower thrusts function effectively, the stability of the operation of the compressor 21 can be improved.

[0101] As described above, by providing the compressor and air conditioner of the present invention, leakage of refrigerant as a fluid, mechanical loss, and wear can be reduced.

[0102] While the compressor and air conditioning apparatus of the present invention have been described in detail using the above-mentioned embodiments, the present invention is not limited to the above-mentioned embodiments and can be modified within the scope of what a person skilled in the art can conceive, including other embodiments, additions, modifications, omissions, and the like, and any aspect is within the scope of the present invention as long as it achieves the functions and effects of the present invention.

[0103] Therefore, according to the present invention, there is provided a compression mechanism including: (1) an electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; first and second bearings rotatably supporting the rotating shaft; a hollow cylinder into which the eccentric part is inserted; and a hollow tubular body which defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating in the compression chamber, wherein the width of a first end face of the cylinder facing the first bearing is greater than the width of a second end face of the cylinder facing the second bearing, and the inner diameter of the cylinder on the first bearing side is set to d 1 The inner diameter of the cylinder on the second bearing side is d 2 The eccentricity, which indicates the distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric part, is e, and the diameter of the first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid that has flowed into the first space formed by the first bearing, the cylindrical body, and the rotating shaft is D. 1 The diameter of the second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D 2In this case, d 1 <d 2 , and D 2 <D 1 , and d 2 -2e≦D 2 It is possible to provide a compressor characterized in that the following holds true.

[0104] According to the present invention, (2) the corners on the inside of the cylinder and on the first bearing side and the second bearing side are chamfered, and when viewed in a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered part of the cylinder on the first bearing side and the area of ​​the part where the end face of the cylinder on the first bearing side and the first pressure range overlap is defined as A 1 The sum of the area of ​​the chamfered portion of the cylinder on the second bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the second bearing side and the second pressure range overlap is A. 2 In this case, A 1 and A 2 It is possible to provide the compressor according to the above (1), characterized in that

[0105] According to the present invention, (3) the corners on the inside of the cylindrical body and on the first bearing side and the second bearing side are chamfered, and in a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered part of the cylindrical body on the first bearing side and the area of ​​the part where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A 3 The sum of the area of ​​the chamfered portion of the cylinder on the second bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the second bearing side and the second pressure range overlap is A. 4 In this case, A 4 3 It is possible to provide the compressor as described above in (1), characterized in that the following holds true.

[0106] According to the present invention, (4) the diameter of the first pressure range is D 1 The diameter of the second pressure range is D 2 The maximum dimension of the first thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric part sliding on the first bearing, is defined as L 1 ​The maximum dimension of the second thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric part sliding on the second bearing, is L 2 In this case, D 1 <2×L 1 , and D 2 <2×L 2 It is possible to provide the compressor according to any one of the above (1) to (3), characterized in that the following holds true:

[0107] According to the present invention, (5) a compression mechanism includes an electric motor, a rotating shaft rotated by the electric motor and having an eccentric part, first and second bearings rotatably supporting the rotating shaft, a hollow cylinder into which the eccentric part is inserted, and a hollow tubular body which defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating in the compression chamber, the inside of the cylinder and the first bearing side and the second bearing side are chamfered, the width of a first end face of the cylinder facing the first bearing is larger than the width of a second end face of the cylinder facing the second bearing, and the inner diameter of the cylinder on the first bearing side is set to d 1 The inner diameter of the cylinder on the second bearing side is d 2 The eccentricity, which indicates the distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric part, is e, and the diameter of the first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid that has flowed into the first space formed by the first bearing, the cylindrical body, and the rotating shaft is D. 1 The diameter of the second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D 2 In this case, d 1 <d 2 , and D 2 <D 1 , and D 2 <d 2 -2e and d 1 -2e≦D 1 is established, and the sum of the area of ​​the chamfered portion of the cylinder on the first bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the first bearing side and the first pressure range overlap in a plan view in the axial direction of the rotating shaft is defined as A 5The sum of the area of ​​the chamfered portion of the cylinder on the second bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the second bearing side and the second pressure range overlap is A. 6 In this case, A 5 and A 6 and are identical to each other.

[0108] According to the present invention, (6) a compression mechanism includes an electric motor, a rotating shaft rotated by the electric motor and having an eccentric part, first and second bearings rotatably supporting the rotating shaft, a hollow cylinder into which the eccentric part is inserted, and a hollow tubular body which defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating in the compression chamber, the inside of the cylinder and the first bearing side and the second bearing side are chamfered, the width of a first end face of the cylinder facing the first bearing is larger than the width of a second end face of the cylinder facing the second bearing, and the inner diameter of the cylinder on the first bearing side is set to d 1 The inner diameter of the cylinder on the second bearing side is d 2 The eccentricity, which indicates the distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric part, is e, and the diameter of the first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid that has flowed into the first space formed by the first bearing, the cylindrical body, and the rotating shaft is D. 1 The diameter of the second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D 2 In this case, d 1 <d 2 , and D 2 <D 1 , and D 2 <d 2 -2e and d 1 -2e≦D 1 is established, and the sum of the area of ​​the chamfered portion of the cylinder on the first bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the first bearing side and the first pressure range overlap in a plan view in the axial direction of the rotating shaft is defined as A 7 The sum of the area of ​​the chamfered portion of the cylinder on the second bearing side and the area of ​​the portion of the cylinder where the end face of the cylinder on the second bearing side and the second pressure range overlap is A. 8In this case, A 8 7 It is possible to provide a compressor characterized in that the following holds true.

[0109] According to the present invention, (7) the maximum dimension of the first thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric part sliding on the first bearing, is defined as L 1 The maximum dimension of the second thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric part sliding on the second bearing, is L 2 In this case, D 1 <2×L 1 , and D 2 <2×L 2 It is possible to provide the compressor according to the above (5) or (6), characterized in that the following holds true:

[0110] According to the present invention, (8) it is possible to provide the compressor according to any one of (1) to (7) above, in which the compression mechanism includes one or more partition plates between the first bearing and the second bearing and has a plurality of compression chambers.

[0111] According to the present invention, it is possible to provide an air conditioner including a compressor according to any one of (1) to (8) above. [Explanation of symbols]

[0112] 10...Air conditioning equipment 11...Indoor unit 12…Indoor heat exchanger 13…Indoor fan 14...Indoor fan drive motor 20...Outdoor unit 21...Compressor 22...Four-way valve 23…Outdoor expansion valve 24…Outdoor heat exchanger 25…Outdoor fan 26...Outdoor fan drive motor 27…Accumulator 28...Control device 30…Motor 30a…Stator​ 30b...Rotor 31…Pin section 31a…Upper pad 31b…Lower pad 32…Shaft 33…Container 34…Main bearing 35…Sub bearing 36…Compression chamber 37…Cylinder 38…Laura 39…Vane 40...Elastic member 41…Suction nozzle 42, 43…space 44…Discharge nozzle 45...Partition plate 50, 51...Groove 52, 53…Beveled parts 54, 56...end face 55...Upper thrust surface 56…Lower thrust surface 58…Discharge port 59…Notch 60…holes 70, 72...plane part 71, 73…overlapping parts

Claims

1. An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １ and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and d ２ −2e≦D ２ The compressor is characterized in that:

2. Corners on the inner side of the cylindrical body and on the first bearing side and the second bearing side are chamfered, In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. １ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ２ In this case, A １ and A ２ 2. The compressor according to claim 1, wherein:

3. Corners on the inner side of the cylindrical body and on the first bearing side and the second bearing side are chamfered, In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. ３ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ４ In this case, A ４ <A ３ 2. The compressor according to claim 1, wherein the following holds true:

4. The diameter of the first pressure range is D １ The diameter of the second pressure range is D ２ and the maximum dimension of the first thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric portion sliding on the first bearing, is L. １ and the maximum dimension of the second thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric portion sliding on the second bearing, is L. ２ In this case, D １ <2×L １ , and D ２ <2×L ２ 2. The compressor according to claim 1, wherein the following holds true:

5. An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, The inside of the cylindrical body and the first bearing side and the second bearing side are chamfered, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １ and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and D ２ <d ２ -2e and d １ −2e≦D １ holds, and In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. ５ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ６ In this case, A ５ and A ６ and are identical to each other.

6. An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, The inside of the cylindrical body and the first bearing side and the second bearing side are chamfered, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １ and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and D ２ <d ２ -2e and d １ −2e≦D １ holds, and In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. ７ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ８ In this case, A ８ <A ７ The compressor is characterized in that:

7. The maximum dimension of a first thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric portion sliding on the first bearing, is defined as L. １ and the maximum dimension of the second thrust surface, which indicates the distance from the center of the cross section of the rotating shaft to the most distant edge of the eccentric portion sliding on the second bearing, is L. ２ In this case, D １ <2×L １ , and D ２ <2×L ２ 7. The compressor according to claim 5 or 6, wherein the following holds true:

8. The compressor according to claim 1 , 5 or 6 , wherein the compression mechanism includes one or more partition plates between the first bearing and the second bearing, and has a plurality of compression chambers.

9. An air conditioning apparatus including a compressor, the compressor comprising: An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and d ２ −2e≦D ２ An air conditioning apparatus characterized in that:

10. An air conditioning apparatus including a compressor, the compressor comprising: An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, The inside of the cylindrical body and the first bearing side and the second bearing side are chamfered, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １ and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and D ２ <d ２ -2e and d １ −2e≦D １ holds, and In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. ５ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ６ In this case, A ５ and A ６ and are the same.

11. An air conditioning apparatus including a compressor, the compressor comprising: An electric motor; a rotating shaft rotated by the electric motor and having an eccentric part; a compression mechanism including: first and second bearings that rotatably support the rotating shaft; a hollow cylinder into which the eccentric portion is inserted; and a hollow tubular body that defines a compression chamber together with the first and second bearings and compresses a fluid by the cylinder rotating within the compression chamber; Including, The inside of the cylindrical body and the first bearing side and the second bearing side are chamfered, A width of a first end face of the cylindrical body facing the first bearing is greater than a width of a second end face of the cylindrical body facing the second bearing, and The inner diameter of the cylindrical body on the first bearing side is d １ The inner diameter of the cylindrical body on the second bearing side is d ２ an eccentricity amount indicating a distance from the center of the cross section of the rotating shaft to the center of the cross section of the eccentric portion is e; a diameter of a first pressure range on the first bearing side of the compression chamber to which pressure is applied by the fluid flowing into a first space formed by the first bearing, the cylindrical body, and the rotating shaft is D; １and the diameter of a second pressure range on the second bearing side of the compression chamber to which pressure is applied by the fluid flowing into the second space formed by the second bearing, the cylindrical body, and the rotating shaft is defined as D ２ In this case, d １ <d ２ , and D ２ <D １ , and D ２ <d ２ -2e and d １ −2e≦D １ holds, and In a plan view in the axial direction of the rotating shaft, the sum of the area of ​​the chamfered portion of the cylindrical body on the first bearing side and the area of ​​the portion of the cylindrical body where the end face of the cylindrical body on the first bearing side and the first pressure range overlap is defined as A. ７ The sum of the area of ​​the chamfered portion of the cylindrical body on the second bearing side and the area of ​​the portion of the cylindrical body where the end face of the second bearing side and the second pressure range overlap is defined as A. ８ In this case, A ８ <A ７ An air conditioning apparatus characterized in that:

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