Compressors and refrigeration cycle equipment

Abstract

Provided is a twin rotary compressor that has a first cylinder in which a first compression chamber is provided and a second cylinder in which a second compression chamber is provided, said twin rotary compressor comprising: a first bearing that is provided on one end surface of the first cylinder; a second bearing that is provided on one end surface of the second cylinder; an intermediate partition plate that is provided between the first cylinder and the second cylinder and that partitions between the first compression chamber and the second compression chamber; a first small-diameter bolt that is inserted through the first bearing, that has a first male screw portion which is screwed into a first female screw portion formed in the first cylinder, and that fastens and fixes the first bearing and the first cylinder; a second small-diameter bolt that is inserted through the second bearing, that has a second male screw portion which is screwed into a second female screw portion formed in the second cylinder, and that fastens and fixes the second bearing and the second cylinder; and a large-diameter bolt that is inserted into a first screw insertion hole which is formed in the first cylinder and a second screw insertion hole which is formed in the second cylinder and that fastens and fixes the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing.

Description

Technical Field

[0001] The present disclosure relates to a compressor that compresses a refrigerant and a refrigeration cycle device.

Background Art

[0002] Conventionally, there is a twin rotary compressor including a first compression mechanism having a front head, a first cylinder, and a middle plate fixed to the inner wall side of a casing, and a second compression mechanism having a rear head, a second cylinder, and a middle plate (see, for example, Patent Document 1). (Reference).

[0003] Six through holes are formed in the front head of Patent Document 1, and six bolt holes are formed in the first cylinder. A first bolt group (six bolts) is screwed into the bolt holes of the first cylinder through the through holes of the front head to fasten and fix the front head and the first cylinder. Six through holes are formed in the rear head, and three bolt holes and three through holes are formed in the second cylinder. A second bolt group (three bolts) is screwed into the bolt holes of the second cylinder through the through holes of the rear head to fasten and fix the rear head and the second cylinder. Three through holes are formed in the middle plate. Through bolts (three bolts) are screwed into the bolt holes of the first cylinder through the through holes of the rear head, the through holes of the second cylinder, and the through holes of the middle plate to fasten and fix the rear head, the second cylinder, the middle plate, and the first cylinder.

[0004] When assembling this twin rotary compressor, after aligning the front head and the first cylinder, the front head and the first cylinder are fastened and fixed by the first bolt group. After aligning the rear head and the second cylinder, the rear head and the second cylinder are fastened and fixed by the second bolt group. Then, the rear head, the second cylinder, the middle plate, and the first cylinder are fastened and fixed by the through bolts.

[0005] Thus, the twin rotary compressor described above has bolt holes (female threads) formed in the first and second cylinders, allowing the group of components fastened and secured between the front head and the first cylinder by the first group of bolts, and the group of components fastened and secured between the rear head and the second cylinder by the second group of bolts, to be easily fastened and secured using through bolts. [Prior art documents] [Patent Documents]

[0006] [Patent Document 1] Japanese Patent Publication No. 2020-2842 [Overview of the project] [Problems that the invention aims to solve]

[0007] However, the twin rotary compressor described in Patent Document 1 has a configuration in which two bolts (a group of first bolts and a through bolt) are screwed into the same bolt hole of one cylinder (the first cylinder). Therefore, compared to the case in which one bolt is screwed into the same bolt hole of one cylinder, it is necessary to make the axial length of the bolt hole longer, which presents the problem of having to make the axial length of the cylinder longer.

[0008] This disclosure was made to solve the above-mentioned problems and aims to provide a twin-rotary type compressor and refrigeration cycle device that can shorten the axial length of the cylinder compared to conventional devices. [Means for solving the problem]

[0009] The compressor according to this disclosure is a twin rotary type compressor comprising, within a container, a compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, an electric motor for driving the compression mechanism, and a rotating shaft connecting the compression mechanism and the electric motor, wherein the compressor comprises, a first bearing provided on one end face of the first cylinder for rotatably supporting the rotating shaft, a second bearing provided on one end face of the second cylinder for rotatably supporting the rotating shaft, an intermediate partition plate provided between the other end face of the first cylinder and the other end face of the second cylinder which are opposite to each other, separating the first compression chamber and the second compression chamber, and, inserted from the first bearing, the first The assembly comprises: a first small-diameter bolt having a first male threaded portion screwed into a first female threaded portion formed in the cylinder, for fastening and fixing the first bearing and the first cylinder; a second small-diameter bolt having a second male threaded portion inserted from the second bearing and screwed into a second female threaded portion formed in the second cylinder, for fastening and fixing the second bearing and the second cylinder; and a large-diameter bolt inserted into a first through-hole formed in the first cylinder and a second through-hole formed in the second cylinder, for fastening and fixing the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing, wherein the diameters of the first male threaded portion and the second male threaded portion are smaller than the diameter of the male threaded portion of the large-diameter bolt. The first bearing is equipped with a first discharge valve that opens and closes a first discharge hole for discharging refrigerant compressed in the first compression chamber. A total of six bolts are provided circumferentially around the axis of the first cylinder in the order of the first small diameter bolt, the large diameter bolt, the large diameter bolt, the large diameter bolt, the first small diameter bolt, and the large diameter bolt. The first discharge hole is located between two of the three large diameter bolts arranged in a row, and the four large diameter bolts are arranged in different regions of the area obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis. It is. Furthermore, the compressor according to this disclosure is a twin rotary type compressor comprising, within a container, a compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, an electric motor for driving the compression mechanism, and a rotating shaft connecting the compression mechanism and the electric motor, wherein the compressor comprises, a first bearing provided on one end face of the first cylinder for rotatably supporting the rotating shaft, a second bearing provided on one end face of the second cylinder for rotatably supporting the rotating shaft, an intermediate partition plate provided between the other end face of the first cylinder and the other end face of the second cylinder that face each other and separates the first compression chamber and the second compression chamber, a first small-diameter bolt inserted from the first bearing and having a first male threaded portion screwed into a first female threaded portion formed in the first cylinder for fastening and fixing the first bearing and the first cylinder, and a second male threaded portion inserted from the second bearing and screwed into a second female threaded portion formed in the second cylinder The device comprises a second small-diameter bolt for fastening and fixing the second bearing and the second cylinder, and a large-diameter bolt inserted into a first screw hole formed in the first cylinder and a second screw hole formed in the second cylinder, for fastening and fixing the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing, wherein the diameters of the first male thread portion and the second male thread portion are smaller than the diameter of the male thread portion of the large-diameter bolt, and a first discharge valve is provided for opening and closing a first discharge hole formed in the first bearing for discharging refrigerant compressed in the first compression chamber, with a total of five bolts provided in the circumferential direction around the axis of the first cylinder in the order of the first small-diameter bolt, the large-diameter bolt, the large-diameter bolt, the first small-diameter bolt, and the large-diameter bolt, with the first discharge hole located between two consecutively arranged large-diameter bolts, and the three large-diameter bolts are located in different regions of the area obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis. Furthermore, the compressor according to this disclosure is a twin rotary type compressor comprising, within a container, a compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, an electric motor for driving the compression mechanism, and a rotating shaft connecting the compression mechanism and the electric motor, the first bearing provided on one end face of the first cylinder and rotatably supporting the rotating shaft, a second bearing provided on one end face of the second cylinder and rotatably supporting the rotating shaft, an intermediate partition plate provided between the other end face of the first cylinder and the other end face of the second cylinder that face each other and separates the first compression chamber and the second compression chamber, a first small-diameter bolt inserted from the first bearing and having a first male screw portion screwed into a first female screw portion formed in the first cylinder, fastening and fixing the first bearing and the first cylinder, and a second small-diameter bolt inserted from the second bearing and formed in the second cylinder The first cylinder has a second small-diameter bolt having a second male threaded portion screwed into a second female threaded portion, and fastens and fixes the second bearing and the second cylinder. The second cylinder has a large-diameter bolt that is inserted into a first screwed-through hole formed in the first cylinder and a second screwed-through hole formed in the second cylinder, and fastens and fixes the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing. The diameters of the first male threaded portion and the second male threaded portion are smaller than the diameter of the male threaded portion of the large-diameter bolt. The first bearing is provided with a first discharge valve that opens and closes a first discharge hole for discharging refrigerant compressed in the first compression chamber. A total of four bolts are provided circumferentially around the axis of the first cylinder in the order of the first small-diameter bolt, the large-diameter bolt, the first small-diameter bolt, and the large-diameter bolt. The two large-diameter bolts are located in different regions of the area obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis.

[0010] Furthermore, the refrigeration cycle system relating to this disclosure includes the above-mentioned compressor, outdoor heat exchanger, throttle device, and indoor heat exchanger. [Effects of the Invention]

[0011] In the compressor and refrigeration cycle device according to this disclosure, the first male thread of the first small-diameter bolt is screwed into the first female thread of the first cylinder, the second male thread of the second small-diameter bolt is screwed into the second female thread of the second cylinder, and a large-diameter bolt is inserted into the first through-hole of the first cylinder and the second through-hole of the second cylinder. In other words, since one bolt is screwed into the same bolt hole of one cylinder, the axial length of the cylinder can be made shorter compared to the case where two bolts are screwed into the same bolt hole of one cylinder. Furthermore, the first bearing and the first cylinder are fastened and fixed by the first male thread of the first small-diameter bolt, which has a smaller diameter than the male thread of the large-diameter bolt, and the first female thread of the first cylinder. In addition, the second bearing and the second cylinder are fastened and fixed by the second male thread of the second small-diameter bolt, which has a smaller diameter than the male thread of the large-diameter bolt, and the second female thread of the second cylinder. For fastening strength, it is desirable that the threading depth of the male thread portion into the cylinder be 0.5 or more of the diameter of the male thread portion. Therefore, when using small-diameter bolts (first small-diameter bolt and second small-diameter bolt) to configure the threading depth of the male thread portion into the first and second cylinders to be 0.5 or more of the diameter of the male thread portion, the threading depth into the first and second cylinders can be reduced compared to when using large-diameter bolts to configure the threading depth into the first and second cylinders to be 0.5 or more of the diameter of the male thread portion. In other words, the threading length of the first and second male thread portions into the first and second cylinders can be shortened, making it possible to shorten the axial length of the first and second cylinders compared to conventional designs. [Brief explanation of the drawing]

[0012] [Figure 1] This is a schematic diagram of a refrigeration cycle system equipped with a compressor according to Embodiment 1. [Figure 2] This is a schematic longitudinal cross-sectional view showing a compressor according to Embodiment 1. [Figure 3] This is a schematic cross-sectional view of the first compression section of the compressor according to Embodiment 1, viewed from above. [Figure 4]It is a schematic cross-sectional view of the second compression part of the compressor according to Embodiment 1 as seen from below. [Figure 5] It is a schematic longitudinal cross-sectional view of the vicinity of the main part of the bearing of the compressor according to Embodiment 1, enlarged. [Figure 6] It is a schematic view of the bearing of the compressor according to Embodiment 1 as seen from above. [Figure 7] It is a schematic view of the second bearing of the compressor according to Embodiment 1 as seen from below. [Figure 8] It is a schematic longitudinal cross-sectional view of the vicinity of the main part of the compression mechanism part of the compressor according to Embodiment 1, enlarged. [Figure 9] It is a schematic view of projecting the second discharge part onto the bearing in FIG. 6. [Figure 10] It is a schematic longitudinal cross-sectional view of the vicinity of the main part of the compression mechanism part of a conventional compressor, enlarged. [Figure 11] It is a schematic longitudinal cross-sectional view of the vicinity of the main part of the compression mechanism part of the compressor according to Embodiment 2, enlarged. [Figure 12] It is a schematic view of the bearing of the compressor according to Embodiment 3 as seen from above. [Figure 13] It is a schematic view of the bearing of the compressor according to Embodiment 4 as seen from above.

Embodiments for Carrying Out the Invention

[0013] Hereinafter, embodiments of the compressor of the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. Also, in the following drawings including FIG. 1, the relationship of the sizes of each component may be different from the actual ones. Further, in the following description, terms indicating directions are appropriately used to facilitate the understanding of the present disclosure, but these are for explaining the present disclosure and do not limit the present disclosure. Examples of terms indicating directions include, for example, "up", "down", "right", "left", "front", or "rear", etc. Note that in some of the drawings, part of the hatching of the cross-sectional view is omitted.

[0014] Embodiment 1. FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus 1 including a compressor 6 according to Embodiment 1. Hereinafter, the refrigeration cycle apparatus 1 including the compressor 6 according to Embodiment 1 will be described with reference to FIG. 1. The refrigeration cycle apparatus 1 is, for example, an air conditioner. The refrigeration cycle apparatus 1 includes an outdoor unit 2 installed outside the air-conditioned space and an indoor unit 3 installed inside the air-conditioned space. The outdoor unit 2 includes a compressor 6, a flow path switching device 7, an outdoor heat exchanger 8, an outdoor blower 9, and an expansion device 10. The indoor unit 3 includes an indoor heat exchanger 11 and an indoor blower 12. Note that the expansion device 10 may be provided in the indoor unit 3 instead of the outdoor unit 2.

[0015] The compressor 6, the flow path switching device 7, the outdoor heat exchanger 8, the expansion device 10, and the indoor heat exchanger 11 are sequentially connected by a refrigerant pipe 5, thereby forming a refrigerant circuit 4 through which the refrigerant circulates.

[0016] The compressor 6 draws in refrigerant in a low-temperature, low-pressure state, compresses the drawn-in refrigerant to a high-temperature, high-pressure state, and discharges it. The flow path switching device 7 is, for example, a four-way valve, and switches between cooling and heating operation by switching the direction of the refrigerant flow. Note that a combination of two-way and three-way valves may be used instead of a four-way valve as the flow path switching device 7. The outdoor heat exchanger 8 functions as an evaporator or condenser, exchanging heat between air and refrigerant to evaporate or condense the refrigerant into a gaseous state. The outdoor heat exchanger 8 functions as an evaporator during heating operation and as a condenser during cooling operation. The outdoor fan 9 is installed near the outdoor heat exchanger 8 and supplies outdoor air to the outdoor heat exchanger 8. The throttling device 10 reduces the pressure of the refrigerant and causes it to expand. The throttling device 10 is, for example, an electronic expansion valve that can adjust the throttling opening. By adjusting the opening, it controls the refrigerant pressure flowing into the indoor heat exchanger 11 during cooling operation and the refrigerant pressure flowing into the outdoor heat exchanger 8 during heating operation. The indoor heat exchanger 11 functions as an evaporator or condenser, exchanging heat between air and refrigerant to vaporize or condense the refrigerant. The indoor heat exchanger 11 functions as a condenser during heating operation and as an evaporator during cooling operation. The indoor blower 12 is installed near the indoor heat exchanger 11 and supplies indoor air to the indoor heat exchanger 11.

[0017] (Operating mode, Cooling operation) Next, the operating modes of the refrigeration cycle device 1 will be explained. First, the cooling operation will be explained. In cooling operation, the flow path switching device 7 is switched so that the discharge side of the compressor 6 and the outdoor heat exchanger 8 are connected, as shown by the dashed line in Figure 1. In cooling operation, the refrigerant drawn into the compressor 6 is compressed by the compressor 6 and discharged in a high-temperature, high-pressure gaseous state. The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 6 passes through the flow path switching device 7 and flows into the outdoor heat exchanger 8, which acts as a condenser. In the outdoor heat exchanger 8, it exchanges heat with the outdoor air supplied by the outdoor fan 9, condenses, and liquefies. The condensed liquid refrigerant flows into the throttling device 10, where it expands and depressurizes to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. The refrigerant, in a two-phase gas-liquid state, flows into the indoor heat exchanger 11, which acts as an evaporator. In the indoor heat exchanger 11, it exchanges heat with the indoor air supplied by the indoor blower 12, evaporating and becoming a gas. At this time, the indoor air is cooled, and cooling is performed in the room. The evaporated refrigerant, in a low-temperature, low-pressure gaseous state, passes through the flow path switching device 7 and is drawn into the compressor 6.

[0018] (Operating mode, heating operation) Next, the heating operation of the refrigeration cycle unit 1 will be described. In heating operation, the flow path switching device 7 is switched so that the discharge side of the compressor 6 and the indoor heat exchanger 11 are connected, as shown by the solid line in Figure 1. In heating operation, the refrigerant drawn into the compressor 6 is compressed by the compressor 6 and discharged in a high-temperature, high-pressure gaseous state. The high-temperature, high-pressure gaseous refrigerant discharged from the compressor 6 passes through the flow path switching device 7 and flows into the indoor heat exchanger 11, which acts as a condenser. In the indoor heat exchanger 11, it exchanges heat with the indoor air supplied by the indoor blower 12, condenses, and liquefies. At this time, the indoor air is heated, and heating is carried out in the room. The condensed liquid refrigerant flows into the throttling device 10, where it expands and depressurizes to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. The refrigerant, in a two-phase gas-liquid state, flows into the outdoor heat exchanger 8, which acts as an evaporator. There, it exchanges heat with the outdoor air supplied by the outdoor fan 9, evaporating and turning into a gas. The evaporated refrigerant, in a low-temperature, low-pressure gaseous state, passes through the flow path switching device 7 and is drawn into the compressor 6.

[0019] Figure 2 is a schematic longitudinal cross-sectional view showing the compressor 6 according to Embodiment 1. Figure 3 is a schematic cross-sectional view of the first compression section 30a of the compressor 6 according to Embodiment 1, viewed from above. Figure 4 is a schematic cross-sectional view of the second compression section 30b of the compressor 6 according to Embodiment 1, viewed from below. Figure 5 is a schematic longitudinal cross-sectional view showing an enlarged view of the area around the main part of the first bearing 40 of the compressor 6 according to Embodiment 1. Figure 6 is a schematic view of the first bearing 40 of the compressor 6 according to Embodiment 1, viewed from above. Figure 7 is a schematic view of the second bearing 50 of the compressor 6 according to Embodiment 1, viewed from below. Figure 8 is a schematic longitudinal cross-sectional view showing an enlarged view of the area around the main part of the compression mechanism section 30 of the compressor 6 according to Embodiment 1. Note that in Figure 6, the first discharge muffler 27 is omitted for the sake of explanation, and in Figure 7, the second discharge muffler 28 is omitted for the sake of explanation. Furthermore, the symbols in parentheses in Figures 6 and 7 indicate the symbols of the bolts inserted into the holes indicated by the symbol to the left of the symbol.

[0020] Next, the compressor 6 will be described in detail. As shown in Figure 2, the compressor 6 comprises a container 20, a discharge pipe 22, a suction section 23, an electric motor section 24, a compression mechanism section 30, a rotating shaft 25, an oil separator 26, a first bearing 40, a second bearing 50, a first discharge muffler 27, and a second discharge muffler 28. In Embodiment 1, the compressor 6 is a twin rotary type compressor having a first cylinder 31 and a second cylinder 71.

[0021] (container 20) The container 20 is a sealed structure that forms the outer shell of the compressor 6, and has an oil reservoir 21 at its bottom where refrigerant oil is stored. Here, the refrigerant oil is supplied to each sliding part of the compressor 6 to lubricate them.

[0022] (Discharge pipe 22) The discharge pipe 22 is located at the top of the container 20 and discharges the compressed refrigerant to the outside of the container 20.

[0023] (Suction part 23) The suction section 23 draws refrigerant into the container 20 and has a suction pipe 23a, an suction muffler 23b, and two outlet pipes 23c. The suction pipe 23a is connected to an accumulator (not shown) and introduces the refrigerant flowing in from the accumulator into the suction muffler 23b. The suction muffler 23b is connected to the suction pipe 23a and separates and stores the liquid refrigerant from the refrigerant flowing in from the suction pipe 23a, and distributes the gaseous refrigerant to each outlet pipe 23c. The two outlet pipes 23c are each connected to the suction muffler 23b and introduce the refrigerant flowing in from the suction muffler 23b into the compression mechanism 30.

[0024] (Electric motor part 24) The motor unit 24 is located in the upper part of the interior of the container 20, and its rotation frequency is changed by inverter control or the like. It has a stator 24a and a rotor 24b. The stator 24a has a cylindrical shape, and its outer surface is fixed to the inner wall of the container 20. A coil (not shown) that is supplied with power from an external power source (not shown) is wound around the stator 24a. The rotor 24b has a cylindrical shape and is arranged at a distance from the inner circumference of the stator 24a. The rotor 24b rotates when power is supplied to the stator 24a.

[0025] (Compression mechanism 30) The compression mechanism 30 is located in the lower part of the inside of the container 20 and compresses the refrigerant. In Embodiment 1, the compression mechanism 30 has an upper first compression section 30a, a lower second compression section 30b, and an intermediate partition plate 34 connecting the first compression section 30a and the second compression section 30b. As shown in Figure 3, the first compression section 30a has a first cylinder 31, a first piston 32, and vanes 33. Also, as shown in Figure 4, the second compression section 30b has a second cylinder 71, a second piston 72, and vanes 73.

[0026] (First cylinder 31) As shown in Figure 3, the first cylinder 31 is an annular member fixed to the inner wall of the container 20, and has an intake hole 31a through which the inhaled refrigerant passes, and a compression hole 31c connected to the intake hole 31a. The first cylinder 31 also has a vane groove 31b into which the vane 33 is attached. Furthermore, the first cylinder 31 has a discharge notch 31d for discharging the compressed refrigerant. The discharge notch 31d is formed to be inclined, for example, 45° with respect to the axial direction of the rotation axis 25. The discharge notch 31d is also formed at a position that is at an angle with respect to the direction in which the vane 33 extends. Note that in Figure 3, the discharge notch 31d is formed at a position that is at an angle with respect to the direction in which the vane 33 extends, opposite to the direction of the intake hole 31a.

[0027] (Piston 1, 32) The first piston 32 is an annular member inserted into the compression hole 31c of the first cylinder 31, with an insertion hole 32a formed inside into which the rotating shaft 25 is inserted. The first piston 32 forms a first compression chamber 35, which is a cylindrical space for compressing the refrigerant, between itself and the first cylinder 31. The axial end of the peripheral edge of the insertion hole 32a of the first piston 32 is a chamfered portion 32b. The first eccentric portion 25a of the rotating shaft 25 is inserted into the insertion hole 32a of the first piston 32. As a result, the first piston 32 rotates eccentrically in conjunction with the rotation of the rotating shaft 25.

[0028] (Bane 33) The vane 33 is a radially extending rod-shaped member attached to the vane groove 31b formed in the first cylinder 31, which presses against the first piston 32 and partitions the first compression chamber 35. The vane 33 also reciprocates radially while sliding inside the vane groove 31b.

[0029] (Intermediate partition plate 34) As shown in Figure 2, the intermediate partition plate 34 is a plate-shaped member provided between the lower end surface of the first cylinder 31 and the upper end surface of the second cylinder 71, which face each other, and separates the first compression chamber 35 from the second compression chamber 75, which will be described later.

[0030] (Second cylinder 71) As shown in Figure 4, the second cylinder 71 is an annular member formed with an intake hole 71a through which the inhaled refrigerant passes and a compression hole 71c connected to the intake hole 71a. The second cylinder 71 also has a vane groove 71b to which the vane 73 is attached. Furthermore, the second cylinder 71 has a discharge notch 71d for discharging the compressed refrigerant. The discharge notch 71d is formed to be inclined, for example, 45° with respect to the axial direction of the rotation axis 25. The discharge notch 71d is also formed at a position that is at an angle with respect to the direction in which the vane 73 extends. Note that in Figure 4, the discharge notch 31d is formed at a position that is at an angle with respect to the direction in which the vane 73 extends, opposite to the direction of the intake hole 71a.

[0031] (2nd piston 72) The second piston 72 is an annular member inserted into the compression hole 71c of the second cylinder 71, with an insertion hole 72a formed inside into which the rotating shaft 25 is inserted. The second piston 72 forms a second compression chamber 75, which is a cylindrical space for compressing the refrigerant, between itself and the second cylinder 71. The axial end of the peripheral edge of the insertion hole 72a of the second piston 72 is a chamfered portion 72b. The second eccentric portion 25b of the rotating shaft 25 is inserted into the insertion hole 72a of the second piston 72. As a result, the second piston 72 rotates eccentrically in conjunction with the rotation of the rotating shaft 25.

[0032] (Rotation axis 25) As shown in Figure 2, the rotating shaft 25 is a cylindrical member located inside the container 20, in the center of the container 20, and connects the electric motor unit 24 and the compression mechanism unit 30. The rotating shaft 25 has a first eccentric portion 25a that is inserted into the insertion hole 32a of the first piston 32, and a second eccentric portion 25b that is inserted into the insertion hole 72a of the second piston 72. The first eccentric portion 25a and the second eccentric portion 25b are cylindrical members that are thicker than the rotating shaft 25, and their center points are eccentric to the center point of the rotating shaft 25. That is, when the rotating shaft 25 rotates, the first eccentric portion 25a and the second eccentric portion 25b rotate eccentrically around the center point of the rotating shaft 25. Thus, the rotating shaft 25 is connected to the motor unit 24 and rotated, transmitting the rotational force of the motor unit 24 to the first piston 32 via the first eccentric portion 25a and to the second piston 72 via the second eccentric portion 25b.

[0033] The first eccentric portion 25a and the second eccentric portion 25b are positioned symmetrically with respect to the center point of the rotating shaft 25, as shown in Figures 3 and 4. In Figure 3, the lower side is the front side of the compressor 6 and the upper side is the rear side of the compressor 6, while in Figure 4, the upper side is the front side of the compressor 6 and the lower side is the rear side of the compressor 6. An oil passage (not shown) extending in the axial direction is formed inside the rotating shaft 25. Oil drawn up from the oil reservoir 21 flows through the oil passage. In addition, multiple oil supply holes (not shown) connected to the oil passage and extending radially from the oil passage are formed inside the rotating shaft 25. Refrigerant oil is introduced to each sliding part through the oil supply holes and lubricates each sliding part.

[0034] (Oil separator 26) As shown in Figure 2, the oil separator 26 is a disc-shaped component with a larger diameter than the rotating shaft 25 and is fitted onto the upper part of the rotating shaft 25. The oil separator 26 blocks the flow path of the gaseous refrigerant containing refrigerant oil as it rises toward the discharge pipe 22, causing the refrigerant and refrigerant oil to collide and separate. As a result, the oil separator 26 causes the separated refrigerant oil to fall to the bottom of the container 20, and guides only the refrigerant to the discharge pipe 22.

[0035] (First bearing 40) As shown in Figure 2, the first bearing 40 is provided on the upper end surface of the first cylinder 31 and rotatably supports the rotating shaft 25. The first bearing 40 is a cylindrical member and has a base portion 41 fixed to the upper end surface of the first cylinder 31 of the first compression portion 30a by a first small-diameter bolt 61 and a large-diameter bolt 63, and a cylindrical portion 42 which is smaller in diameter than the base portion 41 and extends axially from the inner peripheral edge of the base portion 41. The rotating shaft 25 is rotatably supported by being inserted into the inner peripheral portions of the base portion 41 and the cylindrical portion 42.

[0036] As shown in Figures 5 and 6, a first discharge section 43 is provided at the base 41 of the first bearing 40. The first discharge section 43 includes a valve seat 46, a first discharge valve 44, and a first stationary valve 45. The valve seat 46 is the portion where the first discharge hole 46a is formed, which is connected to the discharge notch 31d formed in the first cylinder 31. The first discharge valve 44 is a leaf spring provided on the valve seat 46 and opens and closes the first discharge hole 46a. The first discharge valve 44 opens the first discharge hole 46a when the pressure at the first discharge hole 46a exceeds a predetermined pressure. The first stationary valve 45 holds down the first discharge valve 44. When the pressure at the first discharge hole 46a exceeds a predetermined pressure, the force pressing the first discharge valve 44 on the first stationary valve 45 increases, releasing the pressure on the first discharge valve 44. Hereinafter, the first discharge valve 44 and the first stationary valve 45 will be collectively referred to as the first discharge valve.

[0037] (Second bearing 50) As shown in Figure 2, the second bearing 50 is provided on the lower end surface of the second cylinder 71 and rotatably supports the rotating shaft 25. The second bearing 50 is a cylindrical member and has a base portion 51 fixed to the lower end surface of the second cylinder 71 of the second compression portion 30b by a second small-diameter bolt 62 and a large-diameter bolt 63, and a cylindrical portion 52 which is smaller in diameter than the base portion 51 and extends axially from the inner peripheral edge of the base portion 51. The rotating shaft 25 is rotatably supported by being inserted into the inner peripheral portions of the base portion 51 and the cylindrical portion 52.

[0038] As shown in Figure 7, a second discharge section 53 is provided at the base 51 of the second bearing 50. The second discharge section 53 includes a valve seat (not shown), a second discharge valve 48, and a second stationary valve 49. The valve seat is the portion where the second discharge hole 47a is formed, which is connected to the discharge notch 71d formed in the second cylinder 71. The second discharge valve 48 is a leaf spring provided on the valve seat and opens and closes the second discharge hole 47a. The second discharge valve 48 opens the second discharge hole 47a when the pressure at the second discharge hole 47a exceeds a predetermined pressure. The second stationary valve 49 holds the second discharge valve 48 in place. When the pressure at the second discharge hole 47a exceeds a predetermined pressure, the force pressing the second discharge valve 48 on the second discharge valve 48 increases, releasing the hold on the second discharge valve 48. Hereinafter, the second discharge valve 48 and the second stationary valve 49 will be collectively referred to as the second discharge valve.

[0039] (First discharge muffler 27, second discharge muffler 28) As shown in Figure 2, the first discharge muffler 27 is a dome-shaped member with a hollow section and is attached to the upper surface of the base 41 of the first bearing 40 to suppress noise amplified by resonance occurring in the internal space of the container 20. A hole (not shown) into which the rotating shaft 25 is inserted is formed in the center of the first discharge muffler 27. Bolt holes (not shown) into which bolts are inserted are formed on the outer circumference of the first discharge muffler 27. The second discharge muffler 28 is a dome-shaped member with a hollow section and covers the lower surface of the base 51 of the second bearing 50 and the bottom of the rotating shaft 25 to suppress noise amplified by resonance occurring in the internal space of the container 20. Bolt holes (not shown) into which bolts are inserted are formed on the outer circumference of the second discharge muffler 28.

[0040] (Operation of compressor 6) Next, the operation of the compressor 6 according to Embodiment 1 will be explained using Figures 2 to 4. When power is supplied to the stator 24a, the rotor 24b rotates. As a result, the rotating shaft 25 fixed to the rotor 24b rotates, and the first eccentric portion 25a and the second eccentric portion 25b of the rotating shaft 25 rotate eccentrically. When the first eccentric portion 25a rotates eccentrically, the first piston 32 into which the first eccentric portion 25a is inserted rotates eccentrically inside the compression hole 31c of the first cylinder 31. In addition, the vane 33 attached to the first cylinder 31 moves by moving in and out of the vane groove 31b, and thus partitions the first compression chamber 35 without hindering the eccentric rotation of the first piston 32. Due to the eccentric rotation of the first piston 32, the volume of the first compression chamber 35 gradually decreases, and as a result, the refrigerant inside the first compression chamber 35 is compressed. Similarly, when the second eccentric portion 25b rotates eccentrically, the second piston 72 into which the second eccentric portion 25b is inserted rotates eccentrically inside the compression hole 71c of the second cylinder 71. In addition, the vane 73 attached to the second cylinder 71 moves by moving in and out of the vane groove 71b, and thus partitions the second compression chamber 75 without hindering the eccentric rotation of the second piston 72. As the eccentric rotation of the second piston 72 causes the volume of the second compression chamber 75 to gradually decrease, thereby compressing the refrigerant inside the second compression chamber 75.

[0041] In Embodiment 1, the first eccentric portion 25a and the second eccentric portion 25b are positioned point-symmetrically with respect to the center point of the rotation axis 25, as shown in Figures 3 and 4. In other words, the first eccentric portion 25a and the second eccentric portion 25b are out of phase by 180°. Therefore, the phase angle between the first piston 32 into which the first eccentric portion 25a is inserted and the second piston 72 into which the second eccentric portion 25b is inserted is out of phase by 180°. Consequently, the axial load is reduced, improving the reliability of the compressor 6, and torque fluctuations are reduced, decreasing vibrations in the rotational direction.

[0042] (Refrigerant flow) Next, the flow of refrigerant in the compressor 6 will be explained using Figure 2. The refrigerant drawn in from the suction pipe 23a is separated into gaseous and liquid refrigerant by the suction muffler 23b. Only the gaseous refrigerant then flows through the two outlet pipes 23c into the suction hole 31a formed in the first cylinder 31 and the suction hole 71a formed in the second cylinder 71, respectively. The refrigerant that flows into the suction hole 31a flows out into the first compression chamber 35. The eccentrically rotating first piston 32 continuously reduces the volume of the first compression chamber 35, compressing the refrigerant. Similarly, the refrigerant that flows into the suction hole 71a flows out into the second compression chamber 75. The eccentrically rotating second piston 72 continuously reduces the volume of the second compression chamber 75, compressing the refrigerant.

[0043] The refrigerant, compressed in the first compression chamber 35 to a high temperature and high pressure state, passes through the discharge notch 31d of the first cylinder 31 to the first discharge hole 46a of the first bearing 40. When the pressure at the first discharge hole 46a exceeds a predetermined pressure, the first discharge valve 44 presses the first stationary valve 45, and when the first stationary valve 45 opens, the refrigerant flows out from the first discharge valve 44 into the space between the first discharge muffler 27 and the first bearing 40. The flowing refrigerant flows from the first discharge muffler 27 into the container 20 and through the gap in the motor unit 24 to the discharge pipe 22. The refrigerant that reaches the discharge pipe 22 is discharged into the refrigerant circuit 4 through the discharge pipe 22. Similarly, the refrigerant, compressed in the second compression chamber 75 to a high temperature and high pressure state, passes through the discharge notch 71d of the second cylinder 71 to the second discharge hole 47a of the second bearing 50. When the pressure at the second discharge port 47a exceeds a predetermined pressure, the second discharge valve 48 presses against the second stationary valve 49. When the second stationary valve 49 opens, refrigerant flows out from the second discharge valve 48 into the space between the second discharge muffler 28 and the second bearing 50. The refrigerant that has flowed out flows from the second discharge muffler 28 into the container 20, passes through the gap in the motor unit 24, and reaches the discharge pipe 22. The refrigerant that reaches the discharge pipe 22 is discharged into the refrigerant circuit 4 through the discharge pipe 22.

[0044] (Flow of refrigerant oil) Next, the flow of refrigerant oil in the compressor 6 will be explained using Figure 2. The refrigerant oil stored in the oil reservoir 21 is drawn up into an oil passage (not shown) formed inside the rotating shaft 25 by the rotation of the rotating shaft 25, which acts as a centrifugal pump. The refrigerant oil passing through the oil passage flows into each sliding part through each oil supply hole (not shown). The refrigerant oil then lubricates each sliding part.

[0045] Here, the sliding parts include, for example, the parts where the rotating shaft 25 and the first piston 32 come into contact, the parts where the rotating shaft 25 and the first bearing 40 come into contact, the parts where the rotating shaft 25 and the second bearing 50 come into contact, the parts where the rotating shaft 25 and the intermediate partition plate 34 come into contact, the parts where the first piston 32 and the first cylinder 31 come into contact, the parts where the first piston 32 and the first bearing 40 come into contact, the parts where the first piston 32 and the second bearing 50 come into contact, and the parts where the first piston 32 and the intermediate partition plate 34 come into contact. This prevents damage to the components due to direct contact between components and also prevents refrigerant leakage.

[0046] (Fastening of the compression mechanism 30) As shown in Figure 8, the first small-diameter bolt 61 has a first male threaded portion 61a that is screwed into a first female threaded portion 36 formed in the first cylinder 31. Furthermore, as shown in Figure 6, the first bearing 40 has a first bearing eccentric bolt through hole 57 into which the first male threaded portion 61a of the first small-diameter bolt 61 is inserted. The first male threaded portion 61a of the first small-diameter bolt 61 is inserted through the first bearing eccentric bolt through hole 57 in the first bearing 40 and screwed into the first female threaded portion 36. In this way, the first bearing 40 and the first cylinder 31 are fastened and fixed together by the first small-diameter bolt 61 having the first male threaded portion 61a and the first female threaded portion 36 of the first cylinder 31.

[0047] As shown in Figure 8, the second small-diameter bolt 62 has a second male threaded portion 62a that is screwed into a second female threaded portion 76 formed in the second cylinder 71. Furthermore, as shown in Figure 7, the second bearing 50 has a second bearing eccentric bolt through-hole 87 into which the second male threaded portion 62a of the second small-diameter bolt 62 is inserted. The second male threaded portion 62a of the second small-diameter bolt 62 is inserted through the second bearing eccentric bolt through-hole 87 in the second bearing 50 and screwed into the second female threaded portion 76. In this way, the second bearing 50 and the second cylinder 71 are fastened and fixed together by the second small-diameter bolt 62 having the second male threaded portion 62a and the second female threaded portion 76 of the second cylinder 71.

[0048] Here, the diameter of the first male threaded portion 61a of the first small-diameter bolt 61 and the diameter of the second male threaded portion 62a of the second small-diameter bolt 62 are configured to be the same. However, it is permissible for the diameter of the first male threaded portion 61a of the first small-diameter bolt 61 and the diameter of the second male threaded portion 62a of the second small-diameter bolt 62 to differ within the tolerance range. By using this configuration, the same bolt can be used for both the first small-diameter bolt 61 and the second small-diameter bolt 62, thereby reducing the number of parts.

[0049] As shown in Figure 3, the first cylinder 31 has a first screw hole 91 into which a large-diameter bolt 63 is inserted. As shown in Figure 4, the second cylinder 71 has a second screw hole 93 into which a large-diameter bolt 63 is inserted. As shown in Figure 6, the first bearing 40 has a first bearing female screw portion 56 into which the male screw portion 63a of the large-diameter bolt 63 is screwed, and a first bearing coaxial bolt through hole 58 into which the large-diameter bolt 63 is inserted. In other words, in Embodiment 1, the first bearing 40 corresponds to a nut with a female screw formed inside. As shown in Figure 7, the second bearing 50 has a second bearing female screw portion 86 into which the male screw portion 63a of the large-diameter bolt 63 is screwed, and a second bearing coaxial bolt through hole 88 into which the large-diameter bolt 63 is inserted. In other words, in Embodiment 1, the second bearing 50 corresponds to a nut with a female screw formed inside. In the following, the first bearing female thread portion 56 and the second bearing female thread portion 86 will also be referred to as the third female thread portion.

[0050] A large-diameter bolt 63 is inserted from the first bearing 40 side into the first bearing coaxial bolt through hole 58 of the first bearing 40, the first screw through hole 91 of the first cylinder 31, the second screw through hole 93 of the second cylinder 71, and the second bearing female thread portion 86 of the second bearing 50. These components, arranged in the order of first bearing 40, first cylinder 31, intermediate partition plate 34, second cylinder 71, and second bearing 50 from the axial upper side, are fastened and fixed by the large-diameter bolt 63 having a male thread portion 63a and the second bearing female thread portion 86 of the second bearing 50.

[0051] Furthermore, a large-diameter bolt 63 is inserted from the second bearing 50 side into the first bearing female thread portion 56 of the first bearing 40, the first screw through hole 91 of the first cylinder 31, the second screw through hole 93 of the second cylinder 71, and the second bearing coaxial bolt through hole 88 of the second bearing 50. These components, arranged in the order of first bearing 40, first cylinder 31, intermediate partition plate 34, second cylinder 71, and second bearing 50 from the axial upper side, are fastened and fixed together by the large-diameter bolt 63 having a male thread portion 63a and the first bearing female thread portion 56 of the first bearing 40.

[0052] Thus, in Embodiment 1, there are large-diameter bolts 63 inserted from the first bearing 40 side and large-diameter bolts 63 inserted from the second bearing 50 side. Furthermore, in Embodiment 1, there are two large-diameter bolts 63 inserted from the first bearing 40 side and two large-diameter bolts 63 inserted from the second bearing 50 side, and when the first bearing 40 is viewed from above, the large-diameter bolts 63 inserted from the first bearing 40 side and the large-diameter bolts 63 inserted from the second bearing 50 side are arranged alternately in the circumferential direction.

[0053] Furthermore, as shown in Figure 6, a first bearing refrigerant flow path hole 55 is formed in the first bearing 40. As shown in Figure 7, a second bearing refrigerant flow path hole 85 is formed in the second bearing 50. As shown in Figure 3, a first cylinder refrigerant communication hole 92 is formed in the first cylinder 31. As shown in Figure 4, a second cylinder refrigerant communication hole 94 is formed in the second cylinder 71. The first bearing refrigerant flow path hole 55, the second bearing refrigerant flow path hole 85, the first cylinder refrigerant communication hole 92, and the second cylinder refrigerant communication hole 94 constitute a path for the refrigerant discharged from the second bearing 50 to be discharged through these holes from the same height as the first bearing 40.

[0054] Figure 10 is a schematic longitudinal cross-sectional view showing an enlarged view of the area around the main part of the compression mechanism 130 of a conventional compressor 106. In Embodiment 1, as shown in Figure 8, the diameters of the first small-diameter bolt 61 and the second small-diameter bolt 62 are smaller than the diameter of the large-diameter bolt 63. In contrast, in the conventional compressor 106 shown in Figure 10, the diameters of the first small-diameter bolt 61 and the second small-diameter bolt 62 are the same as the diameter of the large-diameter bolt 63.

[0055] According to Embodiment 1, as shown in Figure 8, the diameter of the first small-diameter bolt 61, the diameter of the second small-diameter bolt 62, the diameter of the hole through which the first small-diameter bolt 61 passes in the first bearing 40, the diameter of the hole through which the second small-diameter bolt 62 passes in the second bearing 50, the diameter of the hole into which the first small-diameter bolt 61 is screwed in the first cylinder 31, and the diameter of the hole into which the second small-diameter bolt 62 is screwed in the second cylinder 71 are smaller than the diameter of the large-diameter bolt 63, the diameter of the hole through which the large-diameter bolt 63 passes in the first bearing 40, the diameter of the hole through which the large-diameter bolt 63 passes in the first cylinder 31, the diameter of the hole through which the large-diameter bolt 63 passes in the intermediate partition plate 34, the diameter of the hole through which the large-diameter bolt 63 passes in the second cylinder 71, and the diameter of the hole into which the large-diameter bolt 63 is screwed in the second bearing 50.

[0056] In this way, the difference between the strength required for the large-diameter bolt 63 to fix all of the first bearing 40, the second bearing 50, the first cylinder 31, and the second cylinder 71, and the strength required for the first small-diameter bolt 61 to fix the first bearing 40 and the first cylinder 31, or the second small-diameter bolt 62 to fix the second bearing 50 and the second cylinder 71, can be adjusted by reducing the diameter of the first small-diameter bolt 61 or the second small-diameter bolt 62. This makes it possible to reduce the diameter of the screw holes or screw fastening holes in the first bearing 40 or the second bearing 50, and thus reduce the space required for the first small-diameter bolt 61 or the second small-diameter bolt 62 in the first bearing 40 or the second bearing 50.

[0057] Furthermore, the first cylinder 31 and the first bearing 40 are fastened together with a first small-diameter bolt 61, and the second cylinder 71 and the second bearing 50 are fastened together with a second small-diameter bolt 62. The fastenings made with the first small-diameter bolt 61 and the fastenings made with the second small-diameter bolt 62 are then fastened together with a large-diameter bolt 63 that penetrates all four components: the first cylinder 31, the first bearing 40, the second cylinder 71, and the second bearing 50. As a result, the fastening holes for the first small-diameter bolt 61 required for fastening the first cylinder 31 and the first bearing 40, or the fastening holes for the second small-diameter bolt 62 required for fastening the second cylinder 71 and the second bearing 50, can be made smaller. Consequently, the space required to provide the above-mentioned fastening holes can be reduced, thus improving the degree of spatial flexibility compared to conventional designs.

[0058] Furthermore, conventionally, two bolts are fastened to the first cylinder 31 or the second cylinder 71 in a manner that faces each other. Therefore, in order to reduce the stress on each bolt and on the first cylinder 31 or the second cylinder 71 to which the bolts are fastened, it is necessary to provide engagement points for both bolts on the first cylinder 31 or the second cylinder 71, which necessitates making the axial length of the first cylinder 31 or the second cylinder 71 longer. However, in Embodiment 1, by fastening a large-diameter bolt 63 that penetrates all four components—the first cylinder 31, the first bearing 40, the second cylinder 71, and the second bearing 50—it is only necessary to provide engagement points for one large-diameter bolt 63 on the first bearing 40 or the second bearing 50, or on a nut member attached to the outside of the first bearing 40 or the second bearing 50. As a result, the amount of engagement required for the non-fastened components can be shortened, and consequently, the axial length of the first cylinder 31 or the second cylinder 71 can be shortened.

[0059] In Embodiment 1, the first bearing 40 and the first cylinder 31 are fastened and fixed together by the first male thread portion 61a of the first small-diameter bolt 61, which has a smaller diameter than the male thread portion 63a of the large-diameter bolt 63, and the first female thread portion 36 formed on the first cylinder 31. For fastening strength, it is desirable that the amount of the first male thread portion 61a is threaded into the first cylinder 31 be 0.5 or more of the diameter of the first male thread portion 61a. Here, the amount of the first male thread portion 61a is threaded into the first cylinder 31 is the length of the first male thread portion 61a inside the first cylinder 31.

[0060] Therefore, for example, if the first small-diameter bolt 61 is used and the amount of threading it into the first cylinder 31 is set to 0.5 or more of the diameter of the first male thread portion 61a, the threading length can be shortened compared to the case where the large-diameter bolt 63 is used and the amount of threading it into the first cylinder 31 is set to 0.5 or more of the diameter of the male thread portion 63a, and as a result, the axial length of the first cylinder 31 can be shortened.

[0061] Furthermore, the diameter of the male threaded portion 63a of the large-diameter bolt 63 is larger than the diameters of the first female threaded portion 36 and the second female threaded portion 76. In other words, the diameters of the first small-diameter bolt 61 and the second small-diameter bolt 62 are smaller than the diameter of the large-diameter bolt 63. Therefore, compared to a compressor in which bolts inserted into the first bearing 40 and the second bearing 50 are the same diameter as the large-diameter bolt 63, for example, the compressor 6 according to Embodiment 1 can use bolts with smaller diameters inserted into the first bearing 40 and the second bearing 50, thereby reducing the space required for the bolts to be placed in the first bearing 40 and the second bearing 50.

[0062] Furthermore, the second bearing 50 has a second bearing female threaded portion 86 into which the male threaded portion 63a of the large-diameter bolt 63 is screwed, and the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50 are fastened and fixed together by the second bearing 50 having the second bearing female threaded portion 86 and the large-diameter bolt 63. In addition, the first bearing 40 has a first bearing female threaded portion 56 into which the male threaded portion 63a of the large-diameter bolt 63 is screwed, and the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50 are fastened and fixed together by the first bearing 40 having the first bearing female threaded portion 56 and the large-diameter bolt 63. As a result, no separate parts such as nuts are required to fasten and fix the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50, and the number of parts constituting the compressor 6 can be reduced.

[0063] Figure 9 is a schematic diagram showing the second discharge section 53 projected onto the first bearing 40 of Figure 6. In Figure 9, the second discharge section 53 is shown with a dashed line. The symbols in parentheses in Figure 9 indicate the symbols of the bolts inserted into the holes indicated by the symbol to its left. As shown in Figure 9, the first discharge section 43 and the second discharge section 53 are arranged opposite each other in the axial direction of the first cylinder 31. Therefore, the area over which bolt holes can be symmetrically arranged in the first bearing 40 and the second bearing 50 can be increased, thereby increasing the degree of freedom in the arrangement of bolt holes, and further, it becomes possible to arrange the first bearing refrigerant flow path holes 55 and the second bearing refrigerant flow path holes 85 over a larger area. In order to obtain the above effect to the fullest extent, it is desirable that the first discharge section 43 and the second discharge section 53 be arranged so that they are entirely opposite each other in the axial direction of the first cylinder 31, but this is not limited to that, and it is sufficient if at least a part of them are arranged to be opposite each other.

[0064] As shown in Figure 6, starting from the first small-diameter bolt 61 at the left end, a total of six bolts are arranged in the circumferential direction (clockwise) with respect to the axis of the first cylinder 31 (the point where the two dashed lines in Figure 6 intersect), in the order of first small-diameter bolt 61, large-diameter bolt 63, large-diameter bolt 63, large-diameter bolt 63, first small-diameter bolt 61, and large-diameter bolt 63, with a total of four large-diameter bolts 63. At the point where three large-diameter bolts 63 are in a row, the first discharge hole 46a is positioned between two of the large-diameter bolts 63. Furthermore, the four large-diameter bolts 63 are positioned in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis of the first cylinder 31 (the two dashed lines in Figure 6).

[0065] Thus, by using not only the large-diameter bolts 63 but also the smaller-diameter first small-diameter bolts 61, the area on which the first discharge port 46a can be positioned can be increased, thereby increasing the flexibility of the positioning of the first discharge port 46a. Furthermore, since the area around the first discharge port 46a, where the highest pressure is reached in the first compression chamber 35, is fixed with three large-diameter bolts 63, insufficient fastening force during high-pressure operation of the compressor 6 can be reduced. In addition, by positioning the four large-diameter bolts 63 that fasten all of the first discharge muffler 27, first bearing 40, first cylinder 31, intermediate partition plate 34, second cylinder 71, second bearing 50, and second discharge muffler 28 in different areas of the area obtained by dividing the first cylinder 31 into four equal parts, they can be fastened and fixed in a balanced manner.

[0066] Furthermore, as shown in Figure 8, the first discharge muffler 27, the first bearing 40, and the first cylinder 31 are fastened and fixed together by the first small-diameter bolt 61 and the first female threaded portion 36 formed on the first cylinder 31. Therefore, the first discharge muffler 27, the first bearing 40, and the first cylinder 31 can be fastened and fixed together using only the small-diameter first small-diameter bolt 61, without relying on the larger diameter large-diameter bolt 63, making assembly easier.

[0067] Furthermore, the second discharge muffler 28, the second bearing 50, and the second cylinder 71 are fastened and fixed together by the second small-diameter bolt 62 and the second female threaded portion 76 formed on the second cylinder 71. Therefore, the second discharge muffler 28, the second bearing 50, and the second cylinder 71 can be fastened and fixed together using only the second small-diameter bolt 62, without relying on the larger diameter bolt 63, making assembly easier.

[0068] Furthermore, in Embodiment 1, the first discharge muffler 27, the first bearing 40, and the first cylinder 31 are aligned, and then the first discharge muffler 27, the first bearing 40, and the first cylinder 31 are fastened and fixed together by the first small-diameter bolt 61. The second discharge muffler 28, the second bearing 50, and the second cylinder 71 are aligned, and then the second discharge muffler 28, the second bearing 50, and the second cylinder 71 are fastened and fixed together by the second small-diameter bolt 62. Subsequently, these components, which are arranged in the order of the first discharge muffler 27, the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, the second bearing 50, and the second discharge muffler 28, are fastened and fixed together by the large-diameter bolt 63.

[0069] The compressor 6 according to Embodiment 1 is a twin rotary type compressor 6 having a compression mechanism 30 having a first cylinder 31 with a first compression chamber 35 inside and a second cylinder 71 with a second compression chamber 75 inside, an electric motor 24 that drives the compression mechanism 30, and a rotating shaft 25 that connects the compression mechanism 30 and the electric motor 24, all housed in a container 20. The compressor 6 is a twin rotary type compressor 6 having a compression mechanism 30 having a first cylinder 31 with a first compression chamber 35 inside and a second cylinder 71 with a second compression chamber 75 inside, housed in a container 20, and includes a first bearing 40 provided on one end face of the first cylinder 31 and supporting the rotating shaft 25 rotatably, a second bearing 50 provided on one end face of the second cylinder 71 and supporting the rotating shaft 25 rotatably, an intermediate partition plate 34 that covers the other end face of the first cylinder 31 and the other end face of the second cylinder 71 facing each other and separates the first compression chamber 35 and the second compression chamber 75, and is inserted from the first bearing 40, and the first cylinder 3 The assembly comprises a first small-diameter bolt 61 having a first male threaded portion 61a screwed into a first female threaded portion 36 formed in 1, which fastens and fixes the first bearing 40 and the first cylinder 31; a second small-diameter bolt 62 having a second male threaded portion 62a inserted from the second bearing 50 and screwed into a second female threaded portion 76 formed in the second cylinder 71, which fastens and fixes the second bearing 50 and the second cylinder 71; and a large-diameter bolt 63 inserted into a first screwed through hole 91 formed in the first cylinder 31 and a second screwed through hole 93 formed in the second cylinder 71, which fastens and fixes the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50, wherein the diameters of the first male threaded portion 61a and the second male threaded portion 62a are smaller than the diameter of the male threaded portion 63a of the large-diameter bolt 63.

[0070] In the compressor 6 according to Embodiment 1, the first male threaded portion 61a of the first small-diameter bolt 61 is screwed into the first female threaded portion 36 of the first cylinder 31, the second male threaded portion 62a of the second small-diameter bolt 62 is screwed into the second female threaded portion 76 of the second cylinder 71, and the large-diameter bolt 63 is inserted into the first through-hole 91 of the first cylinder 31 and the second through-hole 93 of the second cylinder 71. In other words, since one bolt is screwed into the same bolt hole of one cylinder, the axial length of the cylinder can be made shorter compared to the case where two bolts are screwed into the same bolt hole of one cylinder. Furthermore, the first bearing 40 and the first cylinder 31 are fastened and fixed together by the first male threaded portion 61a of the first small-diameter bolt 61, which has a smaller diameter than the male threaded portion 63a of the large-diameter bolt 63, and the first female threaded portion 36 of the first cylinder 31. Furthermore, the second bearing 50 and the second cylinder 71 are fastened and fixed together by the second male thread portion 62a of the second small-diameter bolt 62, which has a smaller diameter than the male thread portion 63a of the large-diameter bolt 63, and the second female thread portion 76 of the second cylinder 71. For fastening strength, it is desirable that the amount of the male thread portion is screwed into the cylinder be 0.5 or more of the diameter of the male thread portion. Therefore, when using small-diameter bolts (first small-diameter bolt 61 and second small-diameter bolt 62) to configure the threading depth of the first male thread portion 61a and second male thread portion 62a to the first cylinder 31 and second cylinder 71 to be 0.5 or more of the diameter of the first male thread portion 61a and second male thread portion 62a, respectively, the threading depth of the first male thread portion 61a and second male thread portion 62a to the first cylinder 31 and second cylinder 71 can be reduced compared to when using a large-diameter bolt 63 to configure the threading depth to the first cylinder 31 and second cylinder 71 to be 0.5 or more of the diameter of the male thread portion 63a, respectively. In other words, since the threading length of the first male thread portion 61a and second male thread portion 62a to the first cylinder 31 and second cylinder 71 can be shortened, the axial length of the first cylinder 31 and second cylinder 71 can be shortened compared to conventional designs.

[0071] Furthermore, in the compressor 6 according to Embodiment 1, the diameter of the first male screw portion 61a and the diameter of the second male screw portion 62a are the same.

[0072] According to the compressor 6 of Embodiment 1, by using this configuration, the same bolt can be used for the first small-diameter bolt 61 and the second small-diameter bolt 62, thereby reducing the number of parts.

[0073] Furthermore, in the compressor 6 according to Embodiment 1, a third female threaded portion is formed in one of the first bearing 40 and the second bearing 50, and the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50 are fastened and fixed together by screwing the male threaded portion 63a of the large-diameter bolt 63 into the third female threaded portion.

[0074] According to the compressor 6 of Embodiment 1, this configuration eliminates the need for separate parts such as nuts to fasten and fix the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50, thereby reducing the number of parts that make up the compressor 6.

[0075] Furthermore, the compressor 6 according to Embodiment 1 includes a first discharge valve that opens and closes a first discharge hole 46a formed in the first bearing 40 for discharging refrigerant compressed in the first compression chamber 35, and a second discharge valve that opens and closes a second discharge hole 47a formed in the second bearing 50 for discharging refrigerant compressed in the second compression chamber 75, with the first discharge valve and the second discharge valve being arranged to face each other in the axial direction.

[0076] According to the compressor 6 of Embodiment 1, this configuration increases the area over which bolt holes can be symmetrically arranged in the first bearing 40 and the second bearing 50, thereby increasing the degree of freedom in the arrangement of bolt holes. Furthermore, it becomes possible to arrange the refrigerant flow holes 55 of the first bearing and the refrigerant flow holes 85 of the second bearing over a larger area.

[0077] Furthermore, in the compressor 6 according to Embodiment 1, a total of six bolts are provided in the circumferential direction around the axis of the first cylinder 31 in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63. Of the three large-diameter bolts 63 arranged in a row, a first discharge hole 46a is located between two of the large-diameter bolts 63, and the four large-diameter bolts 63 are each located in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis.

[0078] According to the compressor 6 of Embodiment 1, by using this configuration, not only large-diameter bolts 63 but also small-diameter first small-diameter bolts 61 can be used, thereby increasing the area on which the first discharge port 46a can be positioned, and thus increasing the degree of freedom in positioning the first discharge port 46a. Furthermore, since the area around the first discharge port 46a, where the highest pressure is reached in the first compression chamber 35, is fixed with three large-diameter bolts 63, insufficient fastening force during high-pressure operation of the compressor 6 can be reduced. In addition, the four large-diameter bolts 63 that fasten all of the first discharge muffler 27, first bearing 40, first cylinder 31, intermediate partition plate 34, second cylinder 71, second bearing 50, and second discharge muffler 28 can be positioned in different areas of the region obtained by dividing the first cylinder 31 into four equal parts, thereby enabling balanced fastening and fixing of these components.

[0079] Furthermore, the compressor 6 according to Embodiment 1 is equipped with a first discharge muffler 27 that suppresses noise generated when refrigerant is discharged from the first discharge port 46a, and the first discharge muffler 27, the first bearing 40, and the first cylinder 31 are fastened and fixed together by a first small-diameter bolt 61 and a first female threaded portion 36.

[0080] According to the compressor 6 of Embodiment 1, this configuration allows the first discharge muffler 27, the first bearing 40, and the first cylinder 31 to be fastened and fixed using only the first small-diameter bolt 61, without relying on the large-diameter bolt 63, making assembly easier.

[0081] Furthermore, the compressor 6 according to Embodiment 1 is equipped with a second discharge muffler 28 that suppresses noise generated when refrigerant is discharged from the second discharge port 47a, and the second discharge muffler 28, the second bearing 50, and the second cylinder 71 are fastened and fixed together by a second small-diameter bolt 62 and a second female threaded portion 76.

[0082] According to the compressor 6 of Embodiment 1, this configuration allows the second discharge muffler 28, the second bearing 50, and the second cylinder 71 to be fastened and fixed using only the second small-diameter bolt 62, without relying on the large-diameter bolt 63, making assembly easier.

[0083] Furthermore, the refrigeration cycle device 1 according to this disclosure comprises the above-mentioned compressor 6, outdoor heat exchanger 8, throttle device 10, and indoor heat exchanger 11.

[0084] According to the refrigeration cycle device 1 of Embodiment 1, the same effect as the compressor 6 described above can be obtained.

[0085] Embodiment 2. The following describes Embodiment 2, but the explanation will be omitted for parts that overlap with Embodiment 1, and the same reference numerals will be used for parts that are the same as or corresponding to Embodiment 1. Furthermore, Embodiment 2 will be described primarily for the differences from Embodiment 1.

[0086] Figure 11 is a schematic longitudinal cross-sectional view showing an enlarged view of the area around the main part of the compression mechanism 30 of the compressor 6 according to Embodiment 2. Embodiment 2 differs from Embodiment 1 in that, in the compressor 6, the fastened member to the large-diameter bolt 63 is a nut 64, rather than the first bearing 40 and the second bearing 50.

[0087] As shown in Figure 11, a nut 64 is provided on the male threaded portion 63a of the large-diameter bolt 63. A female threaded portion 64a is formed on this nut 64, and the male threaded portion 63a of the large-diameter bolt 63 is screwed into the female threaded portion 64a. The large-diameter bolt 63 and the nut 64 fasten and fix these components, which are arranged in the order of the first discharge muffler 27, the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, the second bearing 50, and the second discharge muffler 28. Hereafter, the female threaded portion 64a will also be referred to as the third female threaded portion.

[0088] In this case, if a large-diameter bolt 63 is to be screwed into the first bearing 40 and the second bearing 50 for fastening, it would be necessary to provide threads in the base portion 41 of the first bearing 40 and the base portion 51 of the second bearing 50 for screwing in and fastening the large-diameter bolt 63. However, in Embodiment 2, it is not necessary to provide threads in the base portion 41 of the first bearing 40 and the base portion 51 of the second bearing 50, so the wall thickness of the base portion 41 of the first bearing 40 and the base portion 51 of the second bearing 50 can be reduced accordingly.

[0089] Thus, in Embodiment 2, by fastening the large-diameter bolt 63 to the nut 64 instead of the first bearing 40 and the second bearing 50, it becomes unnecessary to provide threads for fastening the large-diameter bolt 63 to the base 41 of the first bearing 40 and the base 51 of the second bearing 50. As a result, the wall thickness of the base 41 of the first bearing 40 and the base 51 of the second bearing 50 can be reduced, thereby reducing the amount of material used and enabling resource conservation.

[0090] As described above, the compressor 6 according to Embodiment 2 is equipped with a nut 64 having a third female threaded portion formed therein, and the male threaded portion 63a of the large-diameter bolt 63 is screwed into the third female threaded portion to fasten and fix the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, and the second bearing 50.

[0091] According to the compressor 6 of Embodiment 2, this configuration eliminates the need to provide threads for fastening large-diameter bolts 63 to the base 41 of the first bearing 40 and the base 51 of the second bearing 50. As a result, the wall thickness of the base 41 of the first bearing 40 and the base 51 of the second bearing 50 can be reduced, thereby reducing the amount of material used and enabling resource conservation.

[0092] Embodiment 3. The following describes Embodiment 3, but the explanation will be omitted for parts that overlap with Embodiment 1, and the same reference numerals will be used for parts that are the same as or corresponding to Embodiment 1. Furthermore, Embodiment 3 will be described primarily for the differences from Embodiment 1.

[0093] Figure 12 is a schematic diagram of the first bearing 40 of the compressor 6 according to Embodiment 3, viewed from above. For the sake of clarity, the first discharge muffler 27 is not shown in Figure 12. Also, the symbols in parentheses in Figure 12 indicate the symbols of bolts inserted into the holes indicated by the symbols to their left.

[0094] In Embodiment 1, a total of six bolts are arranged circumferentially with respect to the axis of the first cylinder 31 in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63. Where three large-diameter bolts 63 are in a row, the first discharge hole 46a is positioned between two of the large-diameter bolts 63. In contrast, in Embodiment 3, as shown in Figure 12, a total of five bolts are arranged circumferentially (clockwise) with respect to the axis of the first cylinder 31 (the point where the two dashed lines in Figure 12 intersect), starting from the first small-diameter bolt 61 on the left, in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63, with a total of three large-diameter bolts 63. Furthermore, where two large-diameter bolts 63 are located consecutively, the first discharge hole 46a is positioned between the two large-diameter bolts 63. In addition, the three large-diameter bolts 63 are positioned in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis of the first cylinder 31 (the two dashed lines in Figure 12).

[0095] Thus, by using not only the large-diameter bolts 63 but also the small-diameter first bolts 61, the area on which the first discharge holes 46a can be positioned can be increased, thereby increasing the flexibility in positioning the first discharge holes 46a. Furthermore, since the area around the first discharge holes 46a, where the highest pressure is reached in the first compression chamber 35, is fixed with three large-diameter bolts 63, insufficient fastening force during high-pressure operation of the compressor 6 can be reduced.

[0096] Furthermore, in Embodiment 3, compared to Embodiment 1, the number of bolt holes that need to be provided in the first bearing 40 and the second bearing 50 to allow the large-diameter bolt 63 to pass through is reduced by one. As a result, the area on which the first discharge hole 46a can be arranged can be increased, further increasing the degree of freedom in the arrangement of the first discharge hole 46a.

[0097] As described above, the compressor 6 according to Embodiment 3 has a total of five bolts arranged circumferentially around the axis of the first cylinder 31 in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63. A first discharge hole 46a is located between two consecutively arranged large-diameter bolts 63, and the three large-diameter bolts 63 are each located in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis.

[0098] According to the compressor 6 of Embodiment 3, by using this configuration, not only large-diameter bolts 63 but also small-diameter first small-diameter bolts 61 can be used, thereby increasing the area on which the first discharge holes 46a can be arranged, and thus increasing the degree of freedom in the arrangement of the first discharge holes 46a. Furthermore, since the area near the first discharge holes 46a, where the highest pressure is reached in the first compression chamber 35, is fixed with three large-diameter bolts 63, the problem of insufficient fastening force during high-pressure operation of the compressor 6 can be reduced. Moreover, compared to Embodiment 1, the number of bolt holes that need to be provided in the first bearing 40 and the second bearing 50 to allow the large-diameter bolts 63 to pass through is reduced by one, so the area on which the first discharge holes 46a can be arranged can be increased by that amount, further increasing the degree of freedom in the arrangement of the first discharge holes 46a. Furthermore, by positioning the three large-diameter bolts 63 that fasten the first discharge muffler 27, the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, the second bearing 50, and the second discharge muffler 28 in different areas of the four-part division of the first cylinder 31, they can be fastened and secured in a balanced manner.

[0099] Embodiment 4. The following describes Embodiment 4, but the explanation will be omitted for parts that overlap with Embodiment 1, and the same reference numerals will be used for parts that are the same as or corresponding to Embodiment 1. Furthermore, Embodiment 4 will be described primarily for its differences from Embodiment 1.

[0100] Figure 13 is a schematic diagram of the first bearing 40 of the compressor 6 according to Embodiment 4, viewed from above. For the sake of clarity, the first discharge muffler 27 is not shown in Figure 13. Also, the symbols in parentheses in Figure 13 indicate the symbols of bolts inserted into the holes indicated by the symbols to their left.

[0101] In Embodiment 1, a total of six bolts are arranged circumferentially with respect to the axis of the first cylinder 31 in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63. Where three large-diameter bolts 63 are in a row, the first discharge hole 46a is positioned between two of the large-diameter bolts 63. In contrast, in Embodiment 4, as shown in Figure 13, a total of four bolts are arranged circumferentially (clockwise) with respect to the axis of the first cylinder 31 (the point where the two dashed lines in Figure 13 intersect), starting from the first small-diameter bolt 61 in the upper left, in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63, with a total of two large-diameter bolts 63. The two large-diameter bolts 63 are positioned in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis of the first cylinder 31 (the two dashed lines in Figure 13).

[0102] In Embodiment 4, compared to Embodiment 1, the number of bolt holes that need to be provided in the first bearing 40 and the second bearing 50 to allow the large-diameter bolt 63 to pass through is reduced by two. As a result, the area on which the first discharge hole 46a can be arranged can be increased, further increasing the degree of freedom in the arrangement of the first discharge hole 46a.

[0103] As described above, the compressor 6 according to Embodiment 4 has a total of four bolts arranged in the order of a first small-diameter bolt 61, a large-diameter bolt 63, a first small-diameter bolt 61, and a large-diameter bolt 63 in the circumferential direction with respect to the axis of the first cylinder 31, and the two large-diameter bolts 63 are arranged in different regions of the area obtained by dividing the first cylinder 31 into four equal parts by a straight line passing through the axis.

[0104] According to the compressor 6 of Embodiment 4, this configuration reduces the number of bolt holes required in the first bearing 40 and the second bearing 50 to allow the large-diameter bolts 63 to pass through by two compared to Embodiment 1. This increases the area available for arranging the first discharge holes 46a, thereby further increasing the flexibility in arranging the first discharge holes 46a. Furthermore, the two large-diameter bolts 63 that fasten the first discharge muffler 27, the first bearing 40, the first cylinder 31, the intermediate partition plate 34, the second cylinder 71, the second bearing 50, and the second discharge muffler 28 can be positioned in different areas of the four-part division of the first cylinder 31, allowing them to be fastened and secured in a balanced manner.

[0105] In the compressor 6 according to embodiments 1 to 4 described above, there is a configuration in which a large-diameter bolt 63 is inserted from the first bearing 40 side and a large-diameter bolt 63 is inserted from the second bearing 50 side, but the compressor 6 is not limited to this. In the compressor 6 according to embodiments 1 to 4 described above, the large-diameter bolt 63 may be inserted only from the first bearing 40 side, or the large-diameter bolt 63 may be inserted only from the second bearing 50 side.

[0106] Furthermore, in the compressor 6 according to the above embodiments 1 to 4, two outlet pipes 23c are provided, with one outlet pipe 23c connected to the first compression chamber 35 of the first compression section 30a and the other outlet pipe 23c connected to the second compression chamber 75 of the second compression section 30b, but the compressor 6 is not limited to this configuration. In the compressor 6 according to the above embodiments 1 to 4, only one outlet pipe 23c may be provided, with the outlet pipe 23c connected to the first compression chamber 35 of the first compression section 30a, and a refrigerant supply from the outlet pipe 23c to the second compression chamber 75 of the second compression section 30b may be branched from the flow path from the outlet pipe 23c to the first compression chamber 35 of the first compression section 30a. Alternatively, the system may be configured to have only one outlet pipe 23c, which is connected to the second compression chamber 75 of the second compression section 30b. The flow path from the outlet pipe 23c to the second compression chamber 75 of the second compression section 30b is branched off, and refrigerant is supplied from the outlet pipe 23c to the first compression chamber 35 of the first compression section 30a. [Explanation of Symbols]

[0107] 1 Refrigeration cycle unit, 2 Outdoor unit, 3 Indoor unit, 4 Refrigerant circuit, 5 Refrigerant piping, 6 Compressor, 7 Flow path switching device, 8 Outdoor heat exchanger, 9 Outdoor fan, 10 Throttle device, 11 12 Indoor heat exchanger, 20 Indoor blower, 21 Container, 22 Oil reservoir, 23 Discharge pipe, 23 Intake section, 23a Intake pipe, 23b Intake muffler, 23c Outlet pipe, 24 Motor section, 24a Stator, 24b Rotor, 25 Rotating shaft, 25a First eccentric section, 25b Second eccentric section, 26 Oil separator, 27 First discharge muffler, 28 Second discharge muffler, 30 Compression mechanism section, 30a First compression section, 30b Second compression section, 31 First cylinder, 31a Intake hole, 31b Vane groove, 31c Compression hole, 31d Discharge notch, 32 First piston, 32a Insertion hole, 32b Chamfered section, 33 Vane, 34 Intermediate partition plate, 35 First compression chamber, 36 First female thread section, 40 1st bearing, 41 base, 42 cylindrical part, 43 1st discharge part, 44 45 First discharge valve, 46 First stationary valve, 46 Valve seat, 46a First discharge hole, 47a Second discharge hole, 48 Second discharge valve, 49 Second stationary valve, 50 Second bearing, 51 Base, 52 Cylinder, 53 Second discharge section, 55 First bearing refrigerant flow path hole, 56 First bearing female thread section, 57 First bearing eccentric bolt through hole, 58 First bearing coaxial bolt through hole, 60 Compressor, 61 First small diameter bolt, 61a First male thread section, 62 Second small diameter bolt, 62a Second male thread section, 63 Large diameter bolt, 63a Male thread section, 64 Nut, 64a Female thread section, 71 Second cylinder, 71a Intake hole, 71b Vane groove, 71c Compression hole, 71d Discharge notch, 72 Second piston, 72a Insertion hole, 72b Chamfered section, 73 Vane, 75 76 Second compression chamber, 85 Second female threaded section, 86 Second bearing refrigerant flow path hole, 86 Second bearing female threaded section, 87 Second bearing eccentric bolt through hole, 88 Second bearing coaxial bolt through hole, 91 First screw through hole, 92 First cylinder refrigerant communication hole, 93 Second screw through hole, 94 Second cylinder refrigerant communication hole, 106 Compressor, 130 Compression mechanism section.

Claims

1. A compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, The motor unit that drives the compression mechanism, A twin rotary type compressor having a rotating shaft connecting the compression mechanism and the electric motor within a container, A first bearing is provided on one end face of the first cylinder and rotatably supports the rotating shaft, A second bearing is provided on one end face of the second cylinder and rotatably supports the rotating shaft, An intermediate partition plate is provided between the other end face of the first cylinder and the other end face of the second cylinder, which are opposite to each other, and separates the first compression chamber and the second compression chamber. A first small-diameter bolt is inserted from the first bearing and has a first male threaded portion that is screwed into a first female threaded portion formed on the first cylinder, and fastens and fixes the first bearing and the first cylinder together. A second small-diameter bolt is inserted from the second bearing and has a second male threaded portion that is screwed into a second female threaded portion formed in the second cylinder, and fastens and secures the second bearing and the second cylinder together. The device comprises a large-diameter bolt inserted into a first screw hole formed in the first cylinder and a second screw hole formed in the second cylinder, which fastens and secures the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing. The diameters of the first male threaded portion and the second male threaded portion are smaller than the diameter of the male threaded portion of the large-diameter bolt. The first bearing is formed and includes a first discharge valve that opens and closes a first discharge hole for discharging the refrigerant compressed in the first compression chamber, Six bolts are provided around the axis of the first cylinder in the circumferential direction, in the order of the first small-diameter bolt, the large-diameter bolt, the large-diameter bolt, the first small-diameter bolt, and the large-diameter bolt. Of the three large-diameter bolts arranged in a row, the first discharge hole is positioned between two of the large-diameter bolts. The four large-diameter bolts are positioned in different areas within the region obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis. Compressor.

2. A compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, The motor unit that drives the compression mechanism, A twin rotary type compressor having a rotating shaft connecting the compression mechanism and the electric motor within a container, A first bearing is provided on one end face of the first cylinder and rotatably supports the rotating shaft, A second bearing is provided on one end face of the second cylinder and rotatably supports the rotating shaft, An intermediate partition plate is provided between the other end face of the first cylinder and the other end face of the second cylinder, which are opposite to each other, and separates the first compression chamber and the second compression chamber. A first small-diameter bolt is inserted from the first bearing and has a first male threaded portion that is screwed into a first female threaded portion formed on the first cylinder, and fastens and fixes the first bearing and the first cylinder together. A second small-diameter bolt is inserted from the second bearing and has a second male threaded portion that is screwed into a second female threaded portion formed in the second cylinder, and fastens and secures the second bearing and the second cylinder together. The device comprises a large-diameter bolt inserted into a first screw hole formed in the first cylinder and a second screw hole formed in the second cylinder, which fastens and secures the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing. The diameters of the first male threaded portion and the second male threaded portion are smaller than the diameter of the male threaded portion of the large-diameter bolt. The first bearing is formed and includes a first discharge valve that opens and closes a first discharge hole for discharging the refrigerant compressed in the first compression chamber, A total of five bolts are provided around the axis of the first cylinder in the circumferential direction, in the order of the first small-diameter bolt, the large-diameter bolt, the large-diameter bolt, the first small-diameter bolt, and the large-diameter bolt. The first discharge hole is positioned between the two large-diameter bolts arranged in a row. The three large-diameter bolts are positioned in different areas within the region obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis. Compressor.

3. A compression mechanism having a first cylinder with a first compression chamber inside and a second cylinder with a second compression chamber inside, The motor unit that drives the compression mechanism, A twin rotary type compressor having a rotating shaft connecting the compression mechanism and the electric motor within a container, A first bearing is provided on one end face of the first cylinder and rotatably supports the rotating shaft, A second bearing is provided on one end face of the second cylinder and rotatably supports the rotating shaft, An intermediate partition plate is provided between the other end face of the first cylinder and the other end face of the second cylinder, which are opposite to each other, and separates the first compression chamber and the second compression chamber. A first small-diameter bolt is inserted from the first bearing and has a first male threaded portion that is screwed into a first female threaded portion formed on the first cylinder, and fastens and fixes the first bearing and the first cylinder together. A second small-diameter bolt is inserted from the second bearing and has a second male threaded portion that is screwed into a second female threaded portion formed in the second cylinder, and fastens and secures the second bearing and the second cylinder together. The device comprises a large-diameter bolt inserted into a first screw hole formed in the first cylinder and a second screw hole formed in the second cylinder, which fastens and secures the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing. The diameters of the first male threaded portion and the second male threaded portion are smaller than the diameter of the male threaded portion of the large-diameter bolt. The first bearing is formed and includes a first discharge valve that opens and closes a first discharge hole for discharging the refrigerant compressed in the first compression chamber, A total of four bolts are provided around the axis of the first cylinder in the circumferential direction, in the order of the first small-diameter bolt, the large-diameter bolt, the first small-diameter bolt, and the large-diameter bolt. The two large-diameter bolts are positioned in different regions of the area obtained by dividing the first cylinder into four equal parts by a straight line passing through the axis. Compressor.

4. The diameter of the first male threaded portion and the diameter of the second male threaded portion are the same. A compressor according to any one of claims 1 to 3.

5. A third female threaded portion is formed in one of the first bearing and the second bearing. The male threaded portion of the large-diameter bolt is screwed into the third female threaded portion, thereby fastening and fixing the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing together. A compressor according to any one of claims 1 to 3.

6. A nut is provided which has a third female threaded portion formed therein. The male threaded portion of the large-diameter bolt is screwed into the third female threaded portion, thereby fastening and fixing the first bearing, the first cylinder, the intermediate partition plate, the second cylinder, and the second bearing together. A compressor according to any one of claims 1 to 3.

7. The second bearing is formed in the second bearing and comprises a second discharge valve that opens and closes a second discharge hole for discharging the refrigerant compressed in the second compression chamber, The first discharge valve and the second discharge valve are arranged to face each other in the axial direction. A compressor according to any one of claims 1 to 3.

8. The system includes a first discharge muffler that suppresses the noise generated when the refrigerant is discharged from the first discharge port. The first discharge muffler, the first bearing, and the first cylinder are fastened and fixed together by the first small-diameter bolt and the first female threaded portion. A compressor according to any one of claims 1 to 3.

9. The system is equipped with a second discharge muffler that suppresses the noise generated when the refrigerant is discharged from the second discharge port, The second discharge muffler, the second bearing, and the second cylinder are fastened and fixed together by the second small-diameter bolt and the second female threaded portion. The compressor according to claim 7.

10. A compressor, outdoor heat exchanger, throttling device, and indoor heat exchanger as described in any one of claims 1 to 3. Refrigeration cycle device.

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