Scroll compressor

Abstract

This scroll compressor (1) comprises a housing (6), a drive mechanism (10), a first screw (30), a second screw (40), and a discharge mechanism (20). An intake connection path (69) is formed in the housing (6). Furthermore, a pressure accumulator (15) is housed in the housing (6). The pressure accumulator (15) is connected to the intake connection path (69). Refrigerant is drawn into the pressure accumulator (15) from an outer surface of the housing (6) through the intake connection path (69). The pressure accumulator (15) is fixed to the first screw (30) to allow it to rotate within the housing (6).

Description

TECHNICAL AREA

[0001] The present invention relates to a scroll compressor. TECHNICAL BACKGROUND

[0002] Patent reference 1 discloses a known scroll compressor (hereinafter referred to simply as a compressor). The compressor has a casing, a drive mechanism, a first screw, a second screw, and a discharge mechanism. The casing has a main frame that defines a screw chamber and a low-pressure chamber within the casing. The first screw, the second screw, and the discharge mechanism are housed in the screw chamber. The drive mechanism is housed in the low-pressure chamber. The main frame has an intake passage through which the low-pressure chamber is connected to the screw chamber. The casing has an intake tube through which the low-pressure chamber is connected to the outside of the casing.

[0003] The first screw faces the second screw in the screw chamber. The first and second screws work together to form a compression chamber between them. The first screw has a drive shaft. The drive shaft is rotatably supported by the main frame, extends into the low-pressure chamber, and is fixed to the drive mechanism. The output mechanism is located between the first and second screws.

[0004] In this compressor, the first screw is driven by the drive mechanism to rotate around the drive axis, and the second screw is driven by the first screw and the output mechanism to rotate around the output axis. A refrigerant is drawn from the outside of the casing into the low-pressure chamber through the intake pipe and then into the screw chamber through the intake port. In this compressor, the volume of the compression chamber changes with the rotation of the first screw and the rotation of the second screw, so that the refrigerant in the screw chamber is drawn into the compression chamber and compressed there. Citation list patent literature

[0005] Patent literature 1: Japanese patent application publication no. H04-076287 SUMMARY OF THE INVENTION Technical Problem

[0006] This type of compressor can be used in an air conditioning unit that includes a heat exchanger and similar components. Such an air conditioning unit can experience a problem in that liquid refrigerant from the heat exchanger and similar components can be drawn into the casing along with gaseous refrigerant in its vapor phase when the air conditioning unit switches from cooling to heating operation, for example. If such liquid refrigerant is drawn into the compression chamber and compressed there, the first and second screws can be damaged, reducing the compressor's reliability.

[0007] Therefore, consideration has been given to providing a pressure accumulator in this compressor in order to separate the refrigerant into a gaseous refrigerant and a liquid refrigerant, thereby allowing the gaseous refrigerant to be drawn from the low-pressure chamber into the compression chamber, while preventing the liquid refrigerant from being drawn into the compression chamber.

[0008] However, if a large quantity of liquid refrigerant is stored in the pressure tank due to gas-liquid separation, the liquid refrigerant inside the pressure tank can be carried upwards by the gaseous refrigerant being drawn into the tank. Consequently, the gas-liquid separation in the pressure tank may be insufficient, and some of the liquid refrigerant in the pressure tank may be drawn into the low-pressure chamber and consequently into the compression chamber, along with the gaseous refrigerant.

[0009] The present invention, which has been made in view of the aforementioned problem, is directed to providing a scroll compressor which has excellent reliability. Solution to the problem

[0010] A scroll compressor according to the present invention comprises: a housing; a drive mechanism; a first screw; and a second screw, wherein the drive mechanism, the first worm and the second worm are housed in the casing, and the first screw and the second screw form a compression chamber for compressing a refrigerant, wherein The drive mechanism has the following: a stator that is fixed to the housing; and a rotor that has a cylindrical shape and is rotatable within the stator. a pressure accumulator is housed in the casing the housing has an intake passage through which the refrigerant, which contains lubricating oil, is drawn into the pressure accumulator from an outside of the housing, the refrigerant that has been drawn through the intake passage is separated by the pressure accumulator into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil, The gaseous refrigerant in the pressure accumulator is drawn into the compression chamber through an intake passage, and The pressure accumulator is fixed to at least one component of the components first screw, second screw and rotor, in such a way that the pressure accumulator can be rotated in the housing.

[0011] In the compressor according to the present invention, in addition to the drive mechanism and the first and second screws, the pressure accumulator is housed in the casing. The casing has an intake port, and the refrigerant is drawn into the pressure accumulator from the outside of the casing through this intake port. The refrigerant contains the lubricating oil.

[0012] In the compressor, the pressure accumulator is fixed to at least one component of the first screw, second screw, and rotor, and is rotatable within the housing. This causes the refrigerant drawn into the pressure accumulator to be separated into gaseous and liquid refrigerant under the influence of the centrifugal force of the rotating accumulator. The gaseous refrigerant in the pressure accumulator is drawn into the compression chamber through the intake port and compressed there. The liquid refrigerant, separated from the gaseous refrigerant, tends to remain in the pressure accumulator at its radially outer edge due to centrifugal force.

[0013] This compressor design prevents the liquid refrigerant in the pressure tank from being drawn into the compression chamber, even if a large quantity of liquid refrigerant is present in the pressure tank. Consequently, it is less likely that the compressor will compress the liquid refrigerant in the compression chamber.

[0014] The gaseous refrigerant drawn into the compression chamber may contain some lubricating oil, thus lubricating the chamber. Consequently, the first and second screws in the compressor are less likely to wear out.

[0015] Therefore, the scroll compressor according to the present invention has excellent reliability.

[0016] The housing preferably has a return flow passage through which the lubricating oil in the housing flows into the pressure accumulator.

[0017] This allows the lubricating oil in the housing to flow appropriately into the pressure accumulator through the return passage. This, therefore, allows the lubricating oil in the housing to be appropriately returned to the compression chamber through the pressure accumulator, thus ensuring adequate lubrication of the compression chamber.

[0018] In the compressor according to the present invention, the first screw can be driven by the drive mechanism to rotate about a drive axis. The second screw can be eccentric to the first screw and driven by the first screw and a drive mechanism to rotate about a drive axis. At least one of the first screw and one of the second screw can have an intake passage and a supply passage through which the lubricating oil in the pressure accumulator is supplied to the compression chamber. The supply passage is preferably located outside the intake passage in a radial direction of the first screw and a radial direction of the second screw and is connected to the pressure accumulator.

[0019] In this design, where the first screw is driven to rotate and the second screw is driven to rotate in order to follow the first screw, a co-rotating scroll compressor in which both the first screw and the second screw rotate serves as the compressor according to the present invention.

[0020] The lubricating oil in the pressure accumulator likely collects on its radially outer side, specifically on the radial outer sides of the first and second screws, under the influence of the centrifugal force of the rotating accumulator. In this respect, at least one of the first and second screws of the compressor has a supply passage, located outwards from the intake passage in the radial direction of the first and second screws and connected to the pressure accumulator. This design allows the lubricating oil in the pressure accumulator to be adequately supplied to the compression chamber through the supply passage. Consequently, the compression chamber is adequately lubricated by the lubricating oil.

[0021] In the compressor, some of the liquid refrigerant in the accumulator inevitably flows through the inlet port along with the lubricating oil. However, the heat generated by the first and second screws, as the liquid refrigerant flows towards the compression chamber, evaporates the liquid refrigerant. This prevents the liquid refrigerant in the accumulator from being drawn into the compression chamber through the inlet port.

[0022] In the compressor, the intake passage is located inwards from the supply passage in the radial direction of the first screw and the second screw, and this design appropriately prevents the liquid refrigerant in the pressure accumulator from being drawn into the compression chamber through the intake passage.

[0023] In this design, the pressure accumulator can be fixed to the first screw and an inner circumferential surface of the rotor. The first screw is preferably not in contact with the rotor.

[0024] Even if the rotor is not in contact with the first screw, the rotor's rotation is transferred to the first screw via the pressure accumulator, which is fixed to both the first screw and the rotor, thus driving the first screw to rotate. This means it is unnecessary to directly connect the rotor and the first screw for power transmission, allowing for greater design flexibility in the shape of the first screw in this compressor design.

[0025] The first screw can be fixed to the inner circumferential surface of the rotor. The pressure accumulator is fixed to the first screw and is preferably not in contact with the rotor.

[0026] In this design, it is unnecessary to directly connect the rotor and the pressure accumulator for power transmission. This compressor design therefore allows for greater design flexibility in the shape of the pressure accumulator, thus ensuring an appropriately sized accumulator volume.

[0027] In the compressor according to the present invention, the drive mechanism can further comprise a drive shaft that is fixed to the rotor and rotatable within the housing. The first screw can be fixed to the housing. The second screw can be connected to the drive shaft and rotate relative to the first screw with a rotation of the drive shaft. The pressure accumulator can be fixed to the rotor. The rotor can have an intake port. The pressure accumulator preferably has an outlet port located radially outward from the intake port, through which the lubricating oil in the pressure accumulator flows into the compression chamber.

[0028] This design allows the lubricating oil in the pressure accumulator to be drawn into the compression chamber through the intake passage together with the gaseous refrigerant, and also allows the lubricating oil to be drawn into the compression chamber through the outlet passage.

[0029] The outlet passage is located outside the intake passage in the radial direction of the pressure accumulator, so that the lubricating oil in the pressure accumulator can flow through the outlet passage in a suitable manner. Advantageous effects of the invention

[0030] The scroll compressor according to the present invention has excellent reliability. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a cross-sectional view of a scroll compressor according to a first embodiment. Fig. Figure 2 is a schematic diagram of an air conditioning device comprising the scroll compressor according to the first embodiment and represents the air conditioning device in a cooling operation. Fig. Figure 3 is a schematic diagram of the air conditioning device comprising the scroll compressor according to the first embodiment and represents the air conditioning device in a heating operation. Fig. Figure 4 is a cross-sectional view of a scroll compressor according to a second embodiment. Fig. Figure 5 is a cross-sectional view of a scroll compressor according to a third embodiment. Fig. Figure 6 is a cross-sectional view of a scroll compressor according to a fourth embodiment. DESCRIPTION OF EXAMPLES OF EXECUTION

[0031] The following describes in detail a first to fourth embodiment of the present invention with reference to the drawings. Compressors 1 to 4 according to the first to fourth embodiment are each mounted on a vehicle (not shown). (First embodiment)

[0032] As in Fig. Figure 1 shows, in particular, the compressor 1 according to the first embodiment is a co-rotating scroll compressor. The compressor 1 has a housing 6, a drive mechanism 10, a drive screw 30, a discharge screw 40, a discharge mechanism 20, and a pressure accumulator 15. The drive screw 30 serves, for example, as the first screw of the present invention. The discharge screw 40 serves, for example, as the second screw of the present invention.

[0033] In the present embodiment, the front-back direction and the top-bottom direction of compressor 1 are indicated by a continuous arrow in Fig. 1 is defined. The front-back direction and the top-bottom direction are perpendicular to each other. In the present embodiment, the compressor 1 is mounted on the vehicle such that the lower side of the compressor 1 corresponds to the lower side of the vehicle. It should be noted that the directions are merely an example for convenience of explanation, and the position of the compressor 1 can be changed as appropriate depending on the vehicle on which the compressor 1 is mounted. The same applies to the compressors 2 to 4, which are described in Fig. 4 to 6 are shown.

[0034] As in Fig. As shown in Figure 1, the housing 6 has a housing body 60, a housing cover 61, and an attachment 62. The housing body 60 and the housing cover 61 are made of an aluminum alloy. The attachment 62 is made of resin. The attachment 62 may also be made of an aluminum alloy.

[0035] The housing body 60 is a tubular component with a base and has an outer circumferential wall 60a and a rear wall 60b. The outer circumferential wall 60a has a cylindrical shape centered around a drive axis O1. The drive axis O1 is parallel to the front-to-back direction.

[0036] The rear wall 60b is located at the rear end of the housing body 60. The rear wall 60b is essentially circular and plate-shaped and is perpendicular to the drive axis O1. The outer circumferential edge of the rear wall 60b is connected to the rear end of the outer circumferential wall 60a. The rear wall 60b has a first support section 64 at the center of its inner surface. The first support section 64 is essentially solid and cylindrical, centered around the drive axis O1, and extends forward from the center of the inner surface of the rear wall 60b into the worm chamber 65, which will be described later.

[0037] The first support section 64 has a pin hole 54. The pin hole 54 is formed on the front end face of the first support section 64 and extends straight back within the first support section 64. The pin hole 54 does not extend through the first support section 64 in the front-to-back direction.

[0038] The first support section 64 has an intake connection passage 69 and a return passage 8. The intake connection passage 69 has a main passage 69a and a radial passage 69b. The main passage 69a opens at the rear wall 60b and extends forward from the rear wall 60b in the direction of the drive axis O1 inside the first support section 64. The main passage 69a is spaced from the pin hole 54 in the front-to-back direction and is not connected to the pin hole 54.

[0039] The main passage 69a is connected to a pipe H7. The intake passage 69 is connected to the outside of the housing 6, i.e., the outside of the compressor 1, through the pipe H7. In the first support section 64, the radial passage 69b is located upstream of the return passage 8 and essentially at the center of the first support section 64 in the front-to-back direction. The radial passage 69b is connected to the main passage 69a. The radial passage 69b extends through the first support section 64 from the main passage 69a in the radial direction of the first support section 64 and opens at the outer circumferential surface of the first support section 64.

[0040] The return passage 8 is located at the rear end of the first support section 64 and is connected to the main passage 69a at a position different from that of the radial passage 69b. This allows the return passage 8 to be connected to the intake connection passage 69. In the same way as the radial passage 69b, the return passage 8 extends through the first support section 64 from the main passage 69a in the radial direction of the first support section 64 and opens at the outer circumferential surface of the first support section 64.

[0041] The housing cover 61 is arranged in front of the housing body 60. The housing cover 61 is essentially circular and plate-shaped and is perpendicular to the drive axis O1. The housing cover 61 is fixed to the housing body 60 by a bolt (not shown), with the outer circumferential edge of the housing cover 61 being in contact with the front end of the outer circumferential wall 60a of the housing body 60. Consequently, the housing body 60 is closed at the front by the housing cover 61. The housing body 60 therefore has the worm chamber 65 inside the housing body 60.

[0042] The housing cover 61 has a second support section 67 at the center of the inner surface of the housing cover 61. The second support section 67 has a cylindrical shape centered around the drive axis O1 and extends rearward from the center of the inner surface of the housing cover 61. An outer ring of a needle bearing 14 is fitted into the second support section 67.

[0043] The housing cover 61 has a discharge connection port 68. The discharge connection port 68 is located at the center of the housing cover 61 and extends through the housing cover 61 in the direction of the drive axis O1. The discharge connection port 68 is connected to a discharge chamber 13, which will be described later. The discharge connection port 68 is connected to a pipe H1. The discharge connection port 68 is connected to the outside of the compressor 1 through the pipe H1.

[0044] The mounting 62 is arranged in the worm chamber 65 and attached to the rear wall 60b of the housing body 60. The mounting 62 is plate-shaped and extends perpendicular to the drive axis O1. The mounting 62 has a first guide passage 62a and a second guide passage 62b.

[0045] The first guide passage 62a is formed in the rear surface of the attachment 62, i.e., the surface of the attachment 62 facing the rear wall 60b. Since the attachment 62 is mounted on the rear wall 60b, the first guide passage 62a extends in the radial direction of the housing body 60. The first guide passage 62a is connected to the return passage 8 at the upper end of the first guide passage 62a.

[0046] The second guide passage 62b is formed in the lower section of the attachment 62. The second guide passage 62b opens at the surface of the attachment 62 facing the screw chamber 65 at the front end of the second guide passage 62b and is connected to the first guide passage 62a at the rear end of the second guide passage 62b. The return passage 8 extends through the first guide passage 62a and the second guide passage 62b in connection with the bottom of the screw chamber 65. The attachment 62 need not necessarily be attached to the housing body 60, and the return passage 8 can be in direct communication with the screw chamber 65.

[0047] The drive mechanism 10 is specifically an electric motor and is housed in the worm gear chamber 65. The worm gear chamber 65 serves as a motor chamber in which the drive mechanism 10 is located. The drive mechanism 10 has a stator 17 and a rotor 11. The stator 17 has a stator core 17a and a coil end 17b. The stator core 17a has a cylindrical shape centered around the drive axis O1. The coil end 17b is formed by a section of a coil that is wound around the stator core 17a. The coil end 17b has an annular shape and projects from the stator core 17a in the direction of the drive axis O1. The stator core 17a is fitted to the inner circumferential surface of the outer circumferential wall 60a, so that the stator 17 is fixed to the housing body 60.

[0048] The rotor 11 has a cylindrical shape centered around the drive axis O1 and is arranged inside the stator 17. Although not shown in detail, the rotor 11 is formed from a plurality of permanent magnets corresponding to the stator 17 and a plurality of electromagnetic steel plates for fixing the permanent magnets and the like.

[0049] The drive section 30 is made of an aluminum alloy. The drive screw 30 is housed in the screw chamber 65. The drive screw 30 has a drive screw end plate 31, a drive screw circumferential wall 32, a drive screw body 33, and a cover body 35.

[0050] The drive worm end plate 31 is essentially disc-shaped and is perpendicular to the drive axis O1 and an output axis O2. The output axis O2 is eccentric and parallel to the drive axis O1. That is, the output axis O2 is parallel to the front-back direction.

[0051] The drive worm end plate 31 has opposing surfaces: a front surface 311 facing the housing cover 61; and a rear surface 312 in the worm chamber 65. A first hub 34 extends from the center of the front surface 311 towards the housing cover 61. The first hub 34 has a cylindrical shape centered around the drive axis O1.

[0052] The drive worm end plate 31 has a discharge port 38. The discharge port 38 is formed in the first hub 34 of the drive worm end plate 31 and extends through the drive worm end plate 31 in the front-back direction.

[0053] In the first hub 34, a dispensing diaphragm valve 57 and a holder 58 are fixed to the drive worm end plate 31 by a fixing bolt 59. The dispensing diaphragm valve 57 opens and closes the dispensing port 38, and the holder 58 adjusts the opening degree of the dispensing diaphragm valve 57.

[0054] The drive worm circumferential wall 32 has a cylindrical shape centered around the drive axis O1 and extends parallel to the drive axis O1 and the output axis O2. The drive worm circumferential wall 32 is integrated with the outer circumferential edge of the drive worm end plate 31 at the front end of the drive worm circumferential wall 32, has a cylindrical shape and extends rearward from the drive worm end plate 31.

[0055] The drive worm body 33 is located inside the drive worm circumferential wall 32. The drive worm body 33 is integrated with the drive worm end plate 31 and extends rearward from the rear surface 312 of the drive worm end plate 31 toward the output worm 40, parallel to the drive axis O1 and the output axis O2. Although not shown in detail, the drive worm body 33 has a spirally extending shape centered around the center of the drive worm end plate 31 and extending radially outward from the center of the spiral. The drive worm body 33 is connected to the inner circumferential surface of the drive worm circumferential wall 32 at its outer circumferential edge.

[0056] The cover body 35 is essentially disc-shaped and is perpendicular to the drive axis O1 and the output axis O2. The cover body 35 has essentially the same diameter as the diameter of the drive worm end plate 31 and the diameter of the drive worm circumferential wall 32. The cover body 35 has a front surface 351 and a rear surface 352. The front surface 351 faces the rear surface 312 of the drive worm end plate 31 in the front-to-back direction. The rear surface 352 faces opposite the front surface 351.

[0057] The cover body 35 includes a second hub 36, an intake passage 35a, and a supply passage 35b. The second hub 36 is integrated with the rear surface 352 at its center and extends rearward from the rear surface 352. The second hub 36 has an insertion hole 350. The insertion hole 350 extends through the second hub 36 and the cover body 35 in the direction of the drive axis O1. The second hub 36 has a cylindrical shape centered around the drive axis O1. A plain bearing 51 is arranged in the insertion hole 350. Instead of the plain bearing 51, a ball bearing or the like may be arranged in the insertion hole 350.

[0058] The intake passage 35a extends through the cover body 35 in a front-to-back direction. The supply passage 35b is located outside the intake passage 35a in the radial direction of the cover body 35. The intake passage 35a is not connected to the supply passage 35b. The opening of the intake passage 35a and the opening of the supply passage 35b on the front surface 351 are located outside the opening of the intake passage 35a and the opening of the supply passage 35b on the rear surface 352 in the radial direction of the cover body 35. This means that the intake passage 35a and the supply passage 35b extend outwards from the rear surface 352 to the front surface 351 in the radial direction of the cover body 35.

[0059] A plurality of rings 22 are attached to the cover body 35 at positions radially outside the second hub 36. The rings 22 are arranged at equal intervals in the circumferential direction of the cover body 35, face forward, and surround the second hub 36 and the insertion hole 350. In the present embodiment, the number of rings 22 is six. Fig. 1 represents two of the six rings 22. The same applies to Fig. 4.

[0060] The discharge screw 40, which is in Fig. The component shown in Figure 1 is made of an aluminum alloy. The output screw 40 is housed in the screw chamber 65, and specifically inside the drive screw 30. The output screw 40 has an output screw end plate 41 and an output screw body 43.

[0061] The output screw end plate 41 is essentially disc-shaped and is perpendicular to the drive axis O1 and the output axis O2. The output screw end plate 41 has a front surface 411 and a rear surface 412. The front surface 411 faces the rear surface 312 of the drive screw end plate 31 in the drive screw 30. The rear surface 412 is opposite the front surface 411 and faces the front surface 351 of the cover body 35.

[0062] The output screw end plate 41 has a housing section 41a. The housing section 41a has a shape centered around the output axis O2 and is cylindrically recessed forward from the rear surface 412 of the output screw end plate 41. A bushing 53 is arranged in the housing section 41a. The bushing 53 can be mounted in the housing section 41a via a bearing, such as a plain bearing or a ball bearing.

[0063] An output pin 55 is inserted into the bushing 53. The output pin 55 is inserted into the bushing 53 at its center, i.e., in a position eccentric to the output axis O2. The output pin 55 is made of steel and has a solid cylindrical shape. The output pin 55 projects rearward from the bushing 53, i.e., from the output worm end plate 41.

[0064] A plurality of anti-rotation pins 21 are fixed in the output screw end plate 41 at positions radially outside the housing section 41a, and the anti-rotation pins 21 project rearward from the rear surface 412. Specifically, each anti-rotation pin 21 is fixed in a position facing outward from the housing section 41a and the ring 22. In the output screw end plate 41, the anti-rotation pins 21 are arranged at equal intervals in the circumferential direction of the output screw end plate 41 and surround the housing section 41a and the bushing 53. In the present embodiment, the number of anti-rotation pins 21 is six, corresponding to the number of rings 22. Fig. 1 and Fig. 4 represent two of the six anti-rotation pins 21.

[0065] As in Fig. As shown in Figure 1, the output screw body 43 is integrated with the output screw end plate 41 and extends forward from the front surface 411 of the output screw end plate 41 towards the input screw end plate 31 and parallel to the input axis O1 and the output axis O2. Although not shown in detail, the output screw body 43 has a spirally extending shape centered around the center of the output screw end plate 41 and extending outwards from the center of the spiral shape.

[0066] The output mechanism 20 has the anti-rotation pins 21 and the rings 22. The number of anti-rotation pins 21 and the number of rings 22 of the output mechanism 20 can be changed as appropriate, as long as each of these is three or more.

[0067] The pressure accumulator 15 is a tubular component with a base and has an outer circumferential wall 15a and a rear wall 15b. The outer circumferential wall 15a has a cylindrical shape centered around the drive axis O1. The outer diameter of the outer circumferential wall 15a is essentially the same diameter as the inner diameter of the rotor 11. The rear wall 15b is located at the rear end of the pressure accumulator 15. The rear wall 15b has an essentially circular plate shape and is perpendicular to the drive axis O1. The outer circumferential edge of the rear wall 15b is connected to the rear end of the outer circumferential wall 15a.

[0068] A through-hole 150 is formed through the rear wall 15b in the direction of the drive axis O1 at the center of the rear wall 15b. The inner diameter of the through-hole 150 is slightly larger than the outer diameter of the first support section 64 of the housing body 60.

[0069] In the compressor 1, the front surface 351 of the cover body 35 faces the rear surface 312 of the drive screw end plate 31, and the cover body 35 is in contact with the rear end of the drive screw circumferential wall 32. The drive screw end plate 31, the drive screw circumferential wall 32, and the cover body 35 are connected to one another by a plurality of bolts 50a. Consequently, the drive screw end plate 31, the drive screw circumferential wall 32, and the cover body 35 are integrated together.

[0070] In the compressor 1, the output screw 40 is housed within the input screw 30, and the input screw body 33 engages with the output screw body 43. Each of the anti-rotation pins 21 is inserted into the ring 22. In this way, the input screw 30 is assembled with the output screw 40 in a front-to-back direction, so that the input screw 30 and the output screw 40 interact to form a screw compression unit 100. Specifically, the input screw body 33 engages with the output screw body 43, the anti-rotation pin 21 is inserted into the ring 22, and the input screw end plate 31 and the input screw circumferential wall 32 of the input screw 30 are connected to the cover body 35 by the bolts 50a.

[0071] Assembling the drive screw 30 with the output screw 40 allows the formation of an intake chamber 30a through the drive screw 30 and the output screw 40. This means that the drive screw body 33 and the output screw body 43 are located within the intake chamber 30a. The intake chamber 30a is separated from the screw chamber 65 by the drive screw end plate 31, the drive screw circumferential wall 32, and the cover body 35.

[0072] In the drive screw 30, the cover body 35 is located behind the drive screw body 33, the output screw body 43, and the output screw end plate 41 in the direction of the drive axis O1. Therefore, in the drive screw 30, i.e., in the screw compression section 100, the cover body 35 is located furthest towards the rear in the direction of the drive axis O1.

[0073] In the compressor 1, the pressure accumulator 15 is fixed to the drive screw 30. Specifically, the outer circumferential wall 15a of the pressure accumulator 15 is oriented towards the cover body 35, and the front end of the outer circumferential wall 15a is in contact with the rear surface 352 of the cover body 35. The pressure accumulator 15 is fixed to the cover body 35 by bolts 50b. Therefore, the pressure accumulator 15 is integrated with the drive screw 30.

[0074] Since the pressure accumulator 15 is fixed to the drive screw 30 in this manner, a gas-liquid separation chamber 16 is defined within the pressure accumulator 15 by the outer circumferential wall 15a and the rear wall 15b of the pressure accumulator 15 and the cover body 35. The gas-liquid separation chamber 16 is connected to the intake chamber 30a by the intake passage 35a and the supply passage 35b. Within the pressure accumulator 15, the outer circumferential wall 15a is inserted into the rotor 11 and fixed to the inner circumferential surface of the rotor 11. This means that the pressure accumulator 15 is located inside the rotor 11 and is fixed to both the drive screw 30 and the rotor 11. Therefore, the pressure accumulator 15 is rotatable together with the rotor 11, and the drive screw 30 is also rotatable with the rotation of the pressure accumulator 15.

[0075] The first support section 64 of the housing body 60 is inserted through the through-hole 150 in the rear wall 15b of the pressure accumulator 15. The pressure accumulator 15 is housed in the screw chamber 65 and is rotatably supported in the gas-liquid separation chamber 16 by the first support section 64. The gas-liquid separation chamber 16 is connected to the outside of the compressor 1 through the intake connection passage 69 and the pipe H7. The gas-liquid separation chamber 16 is also connected to the bottom of the screw chamber 65 through the intake connection passage 69, the return passage 8, the first guide passage 62a, and the second guide passage 62b.

[0076] The front section of the first support section 64 is inserted into the sliding bearing 51, i.e., the second hub 36 of the drive worm 30. Consequently, the cover body 35 is rotatably supported by the first support section 64 via the sliding bearing 51.

[0077] In the drive worm 30, the first hub 34 of the drive worm end plate 31 is fitted into the inner ring of the needle bearing 14, whereby the first hub 34 is rotatably supported by the second support section 67 of the housing cover 61 via the needle bearing 14. In this way, the first hub 34 is supported by the second support section 67, so that the discharge chamber 13 is formed from a space defined by the inner circumferential surface of the first hub 34, the housing cover 61, and the drive worm end plate 31 in the housing 6.

[0078] Accordingly, the drive worm 30 is supported by both the first support section 64 and the second support section 67 of the housing 6 in such a way that the drive worm 30 can be rotated around the drive axis O1.

[0079] In the output screw 40, the output pin 55 is inserted into the pin hole 54 of the first support section 64. Consequently, the output screw 40 is rotatably supported by the first support section 64, such that the output screw 40 is rotated about the output axis O2 by the output pin 55. This means that, in contrast to the input screw 30, the output screw 40 is supported only by the first support section 64 of the housing 6, such that the output screw 40 can rotate about the output axis O2.

[0080] The output axis O2 is eccentric to the drive axis O1. The output screw 40 is supported by the housing 6 in such a way that the output screw 40 can rotate around the output axis O2, and is eccentric to the drive screw 30 and housed within it.

[0081] Compressor 1 is used for an air conditioning unit 200, which is located in Fig. 2 and Fig. Figure 3 shows the air conditioning device 200 comprising the compressor 1 and further comprising a condenser 101, an external heat exchanger 102, an evaporator 103, a sensor 104, a first flow diverter valve 105, a second flow diverter valve 106, a first expansion valve 107, a second expansion valve 108, an on / off valve 109, and pipes H1 to H10. The first flow diverter valve 105 and the second flow diverter valve 106 are specifically three-way valves.

[0082] The discharge connection 68 of compressor 1 is connected to an inlet 101a of condenser 101 via pipe H1. An outlet 101b of condenser 101 is connected to the first flow diverter valve 105 via pipe H2. The first flow diverter valve 105 is connected to an inlet 102a of external heat exchanger 102 via pipe H3. An outlet 102b of external heat exchanger 102 is connected to the second flow diverter valve 106 via pipe H4.

[0083] The second flow switching valve 106 is connected to the sensor 104 via pipe H5. The sensor 104 is connected to an inlet 103a of the evaporator 103 via pipe H6. An outlet 103b of the evaporator 103 is connected to the intake passage 69 of the compressor 1 via pipe H7.

[0084] The first flow diverter valve 105 is connected to one end of pipe H8, and the other end of pipe H8 is connected to pipe H6. Pipe H3 is connected to one end of pipe H9, and the other end of pipe H9 is connected to pipe H5. The second flow diverter valve 106 is connected to one end of pipe H10, and the other end of pipe H10 is connected to pipe H7.

[0085] The first expansion valve 107 is located in pipe H3. The second expansion valve 108 is located in pipe H6. The on / off valve 109 is located in pipe H9. Although not shown, the first flow switching valve 105 and the second flow switching valve 106, the first expansion valve 107 and the second expansion valve 108, and the on / off valve 109 in compressor 1 are connected to a control device (not shown) mounted on the vehicle.

[0086] When the air conditioning unit 200 is in cooling mode, as in Fig. As shown in Figure 2, the first flow diverter valve 105 connects pipe H2 and pipe H3 and disconnects pipes H2 and H3 from pipe H8. The second flow diverter valve 106 connects pipe H4 and pipe H5 and disconnects pipes H4 and H5 from pipe H10. The opening degree of the first expansion valve 107 and the opening degree of the second expansion valve 108 are set, and the on / off valve 109 is closed. During cooling operation, the opening degree of the first expansion valve 107 is approximately at its maximum.

[0087] Accordingly, in the air conditioning unit 200, the refrigerant delivered by the compressor 1 flows into the external heat exchanger 102 through pipe H1, condenser 101, pipe H2, and pipe H3 in that order. The heat of the refrigerant is transferred to the air surrounding the external heat exchanger 102, i.e., the air outside the vehicle. In other words, the refrigerant is cooled in the external heat exchanger 102 by transferring its heat to the air outside the vehicle. The refrigerant, from which the heat has been transferred in the external heat exchanger 102, flows from the external heat exchanger 102 into the evaporator 103 through pipe H4, pipe H5, receiver 104, and pipe H6 in that order. At this time, the opening degree of the second expansion valve 108 is set appropriately to adjust the pressure of the refrigerant flowing from the pipe H6 into the evaporator 103.

[0088] The air surrounding the evaporator 103 is cooled by the refrigerant in the evaporator 103 through heat transfer from the surrounding air. The cooled air is supplied to the vehicle compartment, thus cooling the compartment. The refrigerant, from which heat has been transferred in the evaporator 103, flows from the evaporator 103 to the compressor 1 through pipe H7. During cooling operation, the air surrounding the compressor 101 is warmed by heat transfer from the refrigerant flowing through the condenser 101. However, the warmed air is not supplied to the vehicle compartment.

[0089] When the air conditioning unit 200 is in a heating mode, as in Fig. As shown in Figure 3, the first flow diverter valve 105 connects pipe H2 and pipe H8 and disconnects pipes H2 and H8 from pipe H3. The second flow diverter valve 106 connects pipe H4 and pipe H10 and disconnects pipes H4 and H10 from pipe H5. The opening degree of the first expansion valve 107 is set, and the on / off valve 109 is open.

[0090] Accordingly, in the air conditioning unit 200, the refrigerant is discharged from the compressor 1 and flows into the condenser 101 through the pipe H1. The air surrounding the condenser 101 is heated by the refrigerant in the condenser 101 through heat transfer. The heated air is then supplied to the vehicle compartment, thus heating the compartment.

[0091] The refrigerant, from which heat has been transferred in the condenser 101, flows from the condenser 101 into the external heat exchanger 102 through pipe H2, pipe H8, pipe H6, receiver 104, pipe H5, pipe H9, and pipe H3 in that order. At this time, the opening degree of the first expansion valve 107 is appropriately adjusted to regulate the pressure of the refrigerant flowing from pipe H3 into the external heat exchanger 102. The refrigerant in the external heat exchanger 102 is heated by heat transfer from the air outside the vehicle. The refrigerant, to which heat has been transferred in the external heat exchanger 102, then flows from the external heat exchanger 102 into the compressor 1 through pipe H4, pipe H10, and pipe H7 in that order.

[0092] Specifically, in the operation of compressor 1, as in Fig. As shown in Figure 1, the rotor 11 of the drive mechanism 10 causes the pressure accumulator 15 to rotate around the drive axis O1 in the screw chamber 65. The drive screw 30 is also rotated around the drive axis O1 in the screw chamber 65 by the rotation of the pressure accumulator 15. That is, in this compressor, although the rotor 11 is not in contact with the drive screw 30, the rotation of the rotor 11 is transmitted to the drive screw 30 via the pressure accumulator 15.

[0093] In the output mechanism 20, each of the anti-rotation pins 21 slides on the inner circumferential surface of the ring 22 with the rotations of the pressure accumulator 15 and the drive screw 30, allowing the ring 22 to rotate relative to the anti-rotation pin 21 around the axis of the anti-rotation pin 21. Thus, the output mechanism 20 transmits a torque from the drive screw 30 to the output screw 40.

[0094] Accordingly, the output screw 40 is driven by the drive screw 30 and the output mechanism 20 to rotate around the output axis O2. The output mechanism 20 prevents the output screw 40 from rotating around its own axis. Consequently, the output screw 40 rotates around the output axis O2 relative to the drive screw 30. The drive screw body 33 and the output screw body 43 rotate in the intake chamber 30a such that the drive screw body 33 and the output screw body 43 come into contact with each other. The drive screw body 33 and the output screw body 43 therefore form a compression chamber 12 between them.

[0095] The refrigerant is drawn into the gas-liquid separation chamber 16 from the outside of the compressor 1 through the pipe H7 and the intake connection passage 69 by the rotations of the drive screw 30 and the output screw 40, as indicated by the dashed arrow in Fig. 1 is marked. As described above, the refrigerant in the external heat exchanger 102 is cooled when the air conditioning device 200 is in cooling mode. Consequently, during cooling operation, the refrigerant in the external heat exchanger 102 is partially liquefied and stored as a liquid refrigerant in the external heat exchanger 102. In the air conditioning device 200, the external heat exchanger 102 is connected to the compressor 1 via pipe H4, pipe H5, receiver 106, pipe H6, evaporator 103, and pipe H7 during cooling operation, whereas, during heating operation, the external heat exchanger 102 is connected to the compressor 1 via pipe H4, pipe H10, and pipe H7.

[0096] Therefore, when the air conditioning device 200 is switched from cooling to heating operation, the refrigerant drawn into the gas-liquid separation chamber 16 through pipe H7 and intake passage 69 may include not only the gaseous refrigerant, which is a vapor-phase refrigerant, but also the liquid refrigerant stored in the external heat exchanger 102. The refrigerant drawn into the gas-liquid separation chamber 16 through pipe H7 and intake passage 69 contains lubricating oil 18. For example, the cooling operation may be switched to the heating operation during the transition from summer to winter, and the cooling operation may be temporarily switched to the heating operation in summer if the temperature in the vehicle is mistakenly set.

[0097] In compressor 1, the refrigerant is drawn directly from the outside of compressor 1 into the gas-liquid separation chamber 16 through pipe H7 and the intake passage 69. This prevents the refrigerant, which includes the liquid refrigerant, from flowing outside compressor 1 into the screw chamber 65. This therefore reduces the presence of liquid refrigerant in the screw chamber 65.

[0098] In the compressor 1, the pressure accumulator 15 is rotated around the drive axis O1 in the screw chamber 65 by the rotor 11. This causes the refrigerant, which has been drawn into the gas-liquid separation chamber 16, to be suitably separated into the gaseous and liquid refrigerants under the influence of the centrifugal force of the rotating pressure accumulator 15. Due to centrifugal force, the liquid refrigerant, separated from the gaseous refrigerant, tends to remain in the gas-liquid separation chamber 16 on the radially outer side of the pressure accumulator 15, i.e., on the radially outer side of the drive screw 30 and the output screw 40. The lubricating oil 18 tends to remain in the gas-liquid separation chamber 16 in the same way as the liquid refrigerant.

[0099] In the compressor 1, the cover body 35 of the drive screw 30 has the intake passage 35a and the supply passage 35b. This design allows the gaseous refrigerant in the gas-liquid separation chamber 16 to be drawn in a suitable manner from the intake chamber 30a through the intake passage 35a into the compression chamber 12. The compression chamber 12 compresses the gaseous refrigerant while reducing its volume with the rotation of the drive screw 30 and the output screw 40. Thus, the gaseous refrigerant, which has been compressed to a discharge pressure, is discharged from the discharge port 38 into the discharge chamber 13 and is further discharged to the outside of the compressor 1, i.e., to the condenser 101, through the pipe H1, which is connected to the discharge connection port 68.

[0100] In the cover body 35, the intake passage 35a is located inwards of the supply passage 35b in the radial direction of the drive screw 30. This design of the compressor 1 prevents the liquid refrigerant in the gas-liquid separation chamber 16 from being drawn into the compression chamber 12 through the intake passage 30a, even if a large quantity of liquid refrigerant is present in the gas-liquid separation chamber 16. Furthermore, since the intake passage 35a is connected to the gas-liquid separation chamber 16, even if the liquid refrigerant is located in the screw chamber 65, it is not drawn into the intake passage 35a and thus into the compression chamber 12 without first flowing through the gas-liquid separation chamber 16. Therefore, it is less likely that compressor 1 compresses the liquid refrigerant in compression chamber 12.

[0101] The gaseous refrigerant, which has been drawn into the compression chamber 12 through the intake passage 35a, contains a proportion of the lubricating oil 18. The supply passage 35b is located outside the intake passage 35a in the radial direction of the drive screw 30. The supply passage 35b opens to the gas-liquid separation chamber 16 at a position close to the region where the lubricating oil 18 is located in the gas-liquid separation chamber 16. This allows the lubricating oil 18 in the gas-liquid separation chamber 16 to be drawn into the compression chamber 12 through the supply passage 35b in a suitable manner. Consequently, the compression chamber 12 in the compressor 1 is lubricated by the lubricating oil 18. Therefore, wear of the drive screw end plate 31, the drive screw body 33, the output screw end plate 41 and the output screw body 43 of the compressor is less likely.

[0102] The liquid refrigerant in the gas-liquid separation chamber 16 can partially flow through the supply passage 35b, together with the lubricating oil 18. However, as it flows through the supply passage 35b, the liquid refrigerant evaporates due to the heat generated by the drive screw 30 and the output screw 40 when the compressor 1 is operating. Consequently, the compressor 1 appropriately prevents the liquid refrigerant in the gas-liquid separation chamber 16 from being drawn into the compression chamber 12 through the supply passage 35b. The same applies if the liquid refrigerant inevitably flows through the intake passage 35a.

[0103] Therefore, according to the first embodiment of the present invention, the compressor 1 has excellent reliability.

[0104] In particular, in the compressor 1, the first support section 64 has the return passage 8, and the return passage 8, in conjunction with the gas-liquid separation chamber 16, passes through the intake connection passage 69. The return passage 8, in conjunction with the bottom of the screw chamber 65, passes through the first guide passage 62a and the second guide passage 62b of the mounting 62. This design of the compressor 1 allows the lubricating oil 18, which is stored at the bottom of the screw chamber 65, to flow into the gas-liquid separation chamber 16 through the first guide passage 62a, the second guide passage 62b, the return passage 8, and the intake connection passage 69. The lubricating oil 18 is supplied to the compression chamber 12 in a suitable manner through the supply passage 35b. Accordingly, the compression chamber 12 in the compressor 1 is lubricated in a suitable manner.

[0105] In the compressor 1, the pressure accumulator 15 is fixed to the cover body 35 of the drive screw 30 and located inside the rotor 11, and is fixed to the inner circumferential surface of the rotor 11. Therefore, the pressure accumulator 15 is not located entirely outside the rotor 11 within the compressor 1. This design of the compressor 1 reduces the need to extend the housing 6 in the direction of the drive axis O1. Furthermore, the compressor 1 is able to transmit the power of the rotor 11 to the drive screw 30 via the pressure accumulator 15, thus eliminating the need to directly connect the rotor 11 and the drive screw 30 for power transmission. Consequently, this design allows for greater design flexibility of the drive screw 30 of the compressor 1.Therefore, this design of the compressor 1 allows an increase in the diameters of the drive screw 30 and the output screw 40 in order to ensure the volume of the compression chamber 12 in a suitable manner, while reducing the need to increase the diameter of the casing 6 as much as possible. (Second example)

[0106] As in Fig. As shown in Figure 4, compressor 2 according to the second embodiment is a co-rotating scroll compressor, in the same way as compressor 1 according to the first embodiment. Compressor 2 has a pressure accumulator 25 instead of a pressure accumulator 15. In compressor 2, the cover body 35 of the drive screw 30 has a feed passage 35c instead of a feed passage 35b. The feed passage 35c is located outside the intake passage 35a in the radial direction of the cover body 35. The feed passage 35c extends through the cover body 35 in the front-to-back direction and parallel to the drive axis O1.

[0107] The pressure accumulator 25 is a tubular component with a base and has an outer circumferential wall 25a and a rear wall 25b. The outer circumferential wall 25a has a cylindrical shape centered around the drive axis O1. The outer diameter of the outer circumferential wall 25a is larger than that of the outer circumferential wall 15a of the pressure accumulator 15 of the compressor 1 according to the first embodiment and is essentially the same diameter as the outer diameter of the cover body 35. The rear wall 25b is located at the rear end of the pressure accumulator 25 and has an essentially circular plate shape, perpendicular to the drive axis O1. The outer circumferential edge of the rear wall 25b is connected to the rear end of the outer circumferential wall 25a.

[0108] The rear wall 25b has a through-hole 250 at the center of the rear wall 25b. The through-hole 250 has a structure similar to the structure of the through-hole 150 of the pressure accumulator 15, and the through-hole 250 extends through the rear wall 25b in the direction of the drive axis O1.

[0109] In the same way as in the compressor according to the first embodiment, the pressure accumulator 25 in compressor 2 is fixed to the cover body 35 by the bolts 50b. Accordingly, a gas-liquid separation chamber 26 in the pressure accumulator 25 is defined by the outer circumferential wall 25a and the rear wall of the pressure accumulator 25 and the cover body 35. The gas-liquid separation chamber 26 is connected to the intake passage 35a and the supply passage 35c.

[0110] The pressure accumulator 25 is housed in the screw chamber 65 and rotatably supported by the first support section 64. The gas-liquid separation chamber 26 is connected to the outside of the compressor 2 via the intake connection passage 69 and the pipe H7. The gas-liquid separation chamber 26 is also connected to the bottom of the screw chamber 65 via the intake connection passage 69, the return passage 8, the first guide passage 62a, and the second guide passage 62b.

[0111] In the compressor 2, the drive mechanism 10 is located upstream of the pressure accumulator 25 within the screw chamber 65. The drive screw circumferential wall 32 of the drive screw 30 is inserted into the rotor 11 and fixed to the inner circumferential surface of the rotor 11. It should be noted that other components of the compressor 2 according to the second embodiment are the same as those of the compressor 1 according to the first embodiment, and that the components of the second embodiment that correspond to those of the first embodiment are designated with the same reference numerals and are not described further here.

[0112] In the same way as compressor 1 according to the first embodiment, compressor 2 is also used for the air conditioning device 200 (see Fig. 2 and Fig. 3) used. In the compressor 2, the drive screw 30 and the pressure accumulator 25 are rotated around the drive axis O1 in the screw chamber 65 by the rotation of the rotor 11. The refrigerant is drawn into the gas-liquid separation chamber 26 through the pipe H7 and the intake connection passage 69, as indicated by the dashed arrow in Fig. 4, and is separated into the gaseous and liquid refrigerant. The gaseous refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26 are drawn into the compression chamber 12 through the intake passage 35a and the supply passage 35c. The compressor 2 is also capable of exhibiting the same effects as those of the compressor 1 according to the first embodiment.

[0113] In compressor 2, the drive screw circumferential wall 32 is fixed to the inner circumferential surface of the rotor 11, and the pressure accumulator 25 is fixed to the cover body 35 of the drive screw 30. This design of compressor 2 eliminates the need to place the pressure accumulator 25 inside the rotor 11, thereby increasing the design flexibility of the pressure accumulator 25. In compressor 2, the diameter of the pressure accumulator 25 is larger than that of the pressure accumulator 15 of compressor 1 according to the first embodiment, which appropriately ensures the volume of the gas-liquid separation chamber 26. This facilitates centrifugal separation of the liquid refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26.

[0114] Furthermore, the compressor 2 is able to transfer the power of the rotor 11 to the pressure accumulator 25 via the drive screw 30, thus eliminating the need to directly connect the rotor 11 and the pressure accumulator 25 for power transmission. In this respect, the design of the compressor 2 increases the design flexibility of the pressure accumulator 25. (Third embodiment)

[0115] Fig. Figure 5 represents the compressor 3 according to the third embodiment, which has a housing 7, a drive mechanism 80, a fixed screw 90, a movable screw 110, and a pressure accumulator 27. The fixed screw 90 serves, for example, as the first screw of the present invention. The movable screw 110 serves, for example, as the second screw of the present invention.

[0116] The housing 7 has a motor housing 71, a compressor housing 72, a fixed block 73 and an attachment 62. The motor housing 71 forms the rear section of the housing 7, and the compressor housing 72 forms the front section of the housing 7.

[0117] The motor housing 71 has a rear wall 71a and a first circumferential wall 71b. The rear wall 71a is located at the rear end of the motor housing 71 and extends radially along the motor housing 71. The first circumferential wall 71b is connected to the rear wall 71a, has a substantially cylindrical shape, and extends forward from the rear wall 71a. Together with the rear wall 71a and the first circumferential wall 71b, the motor housing 71 has a tubular shape with a bottom and a front opening. The motor housing 71 has a motor chamber 75.

[0118] The motor housing 71 has a support section 71c. The support section 71c extends from the center of the rear wall 71a into the motor chamber 75. At its front end, the support section 71c has a recess 710 that extends rearward. A sliding bearing 39 is arranged in the recess 710.

[0119] The support section 71c has an intake connection passage 76 and a return passage 8a. The intake connection passage 76 has a main passage 76a and a radial passage 76b. The main passage 76a opens at the rear wall 71a and extends forward from the rear wall 71a in the direction of a drive axis O3 inside the support section 71c. The drive axis O3 is parallel to the front-to-back direction. The main passage 76a is spaced from the recess 710 in the front-to-back direction and is not connected to the recess 710.

[0120] The main passage 76a is connected to the pipe H7. The intake passage 76 is connected to the outside of the housing 7, i.e., the outside of the compressor 3, through the pipe H7.

[0121] In the support section 71c, the radial passage 76b is located upstream of the return passage 8a, essentially at the center of the support section 71c in the front-to-back direction. The radial passage 76b is connected to the main passage 76a. The radial passage 76b extends through the support section 71c from the main passage 76a in the radial direction of the support section 71c and opens at the outer circumferential surface of the support section 71c.

[0122] The return passage 8a is located at the rear end of the support section 71c and is connected to the main passage 76a at a position different from that of the radial passage 76b. This allows the return passage 8a to be connected to the intake connection passage 76. In the same way as the radial passage 76b, the return passage 8a extends through the support section 71c from the main passage 76a in the radial direction of the support section 71c and opens at the outer circumferential surface of the support section 71c.

[0123] The compressor housing 72 has a front wall 72a and a second circumferential wall 72b. The front wall 72a is located at the front end of the compressor housing 72 and extends radially along the housing. The second circumferential wall 72b is connected to the front wall 72a, has a cylindrical shape, and extends rearward from the front wall 72a. Together with the front wall 72a and the second circumferential wall 72b, the compressor housing 72 has a tubular shape with a bottom and a rear opening.

[0124] The compressor housing 72 has an oil separation chamber 72c, a first discharge recess 72d, a discharge passage 72e, and a discharge connection port 72f. The oil separation chamber 72c is located at the front of the compressor housing 72 and extends radially along the housing. The first discharge recess 72d is located inside the compressor housing 72 and behind the oil separation chamber 72c, and is recessed forward toward the oil separation chamber 72c. The discharge passage 72e extends in a front-to-back direction and connects the oil separation chamber 72c and the first discharge recess 72d. The discharge connection port 72f is connected to the upper end of the oil separation chamber 72c and opens to the outside of the compressor housing 72. The discharge connection port 72f is connected to the pipe H1. The delivery connection port 72f is connected to the outside of the compressor 3 through the pipe H1.

[0125] The oil separation chamber 72c is fixed to an oil separation cylinder 70. The outer circumferential surface of the oil separation cylinder 70 and the inner circumferential surface of the oil separation chamber 72c form a separator. A filter 77 is arranged in the oil separation chamber 72c below the oil separation cylinder 70.

[0126] The fixed block 73 is arranged between the motor housing 71 and the compressor housing 72. The motor housing 71, the compressor housing 72, and the fixed block 73 are fastened to the side of the compressor housing 72 by a plurality of bolts 78. The fixed block 73 is held between the motor housing 71 and the compressor housing 72 and is fixed to both. The fixed block 73 is located between the motor chamber 75 and the moving screw 110 in the front-to-back direction. Fig. 5 represents one of the bolts 78. The same applies to Fig. 6. The method for fixing the motor housing 71, the compressor housing 72 and the fixed block 73 can be designed as is suitable.

[0127] The fixed block 73 has a hub 73a extending to the rear. The hub 73a has an insertion hole 73b at its distal end. A first radial bearing 45 and a shaft seal component 29 are arranged in the hub 73a. The fixed block 73 has a connecting passage 73c. ​​The connecting passage 73c is located outside the hub 73a within the fixed block 73 and extends through the fixed block 73 in the front-to-back direction. The number of connecting passages 73c can be configured as needed.

[0128] Six anti-rotation pins 47 are fixed to the stationary block 73 and extend forward. The anti-rotation pins 47 are equally spaced from each other in the circumferential direction of the stationary block 73. Fig. 5 and Fig. 6 represent one of the six anti-rotation pins 47.

[0129] As in Fig. As shown in Figure 5, the attachment 62 is located in the motor chamber 75 and is mounted on the rear wall 71a of the motor housing 71. The upper end of the first guide passage 62a of the attachment 62 is connected to the return passage 8a. The second guide passage 62b of the attachment 62 is connected to the bottom of the motor chamber 75. The return passage 8a extends through the first guide passage 62a and the second guide passage 62b, connecting to the bottom of the motor chamber 75. The attachment 62 need not necessarily be mounted on the motor housing 71, and the return passage 8a may be in direct communication with the motor chamber 75.

[0130] The drive mechanism 80 is housed in the motor chamber 75. The drive mechanism 80 has a stator 81, a rotor 82, and a drive shaft 83. The stator 81 has a stator core 81a and a coil end 81b. The rear end of the coil end 81b has an inclined inner surface to prevent engagement with a counterweight 86, which will be described later. Except for the shape of the coil end 81b, the stator core 81a and the coil end 81b have almost the same design as the stator core 17a and the coil end 17b of the compressor 1 according to the first embodiment, so a detailed description is omitted. The stator core 81a is fitted to the inner circumferential surface of the first circumferential wall 71b, so that the stator 81 is fixed to the motor housing 71.

[0131] The rotor 82 has a cylindrical shape centered around the drive axis O3 and is located inside the stator 81. The rotor 82 has a plurality of electromagnetic steel plates 82a, a first end plate 82b, a second end plate 82c, a plurality of bolts 82d, and a permanent magnet (not shown).

[0132] The electromagnetic steel plates 82a are stacked in the direction of the drive axis O3 and house the permanent magnet. The first end plate 82b and the second end plate 82c hold the electromagnetic steel plates 82a between them in the direction of the drive axis O3. The first end plate 82b, the electromagnetic steel plates 82a, and the second end plate 82c are fastened to one another in the direction of the drive axis O3 by the bolts 82d to form the rotor 82.

[0133] The rotor 82 has a plurality of intake passages 84. Specifically, the intake passages 84 extend through the first end plate 82b, the electromagnetic steel plates 82a, and the second end plate 82c in the direction of the drive axis O3 and are therefore formed within the rotor 82. That is, the intake passages 84 extend through the rotor 82 in the direction of the drive axis O3. The intake passages 84 are equidistant from one another in the circumferential direction of the rotor 82. The number of intake passages 84 of the rotor 82 can be configured as is suitable.

[0134] The drive shaft 83 extends forward and backward from the rotor 82 in the direction of the drive axis O3 and is fixed to the rotor 82. At its rear end, the drive shaft 83 is rotatably supported by the support section 71c of the motor housing 71 via the sliding bearing 39.

[0135] The front end section of the drive shaft 83 is inserted into the insertion hole 73b of the fixed block 73 and is located in the hub 73a. The front end section of the drive shaft 83 is rotatably supported in the hub 73a by the first radial bearing 45. Thus, the drive shaft 83 can rotate about the drive axis O3 in the housing 7. The gap between the fixed block 73 and the drive shaft 83 is sealed by the shaft seal component 29.

[0136] An eccentric pin 85 is fixed to a front end face 83a of the drive shaft 83. The eccentric pin 85 is positioned eccentrically relative to the drive axis O3 at the front end face 83a. The drive shaft 83 is inserted into the insertion hole 73b, so that the eccentric pin 85 is located in the hub 73a. The eccentric pin 85 fits into a bushing 49 in the hub 73a.

[0137] The drive shaft 83 is formed integrally with the counterweight 86. The counterweight 86 is positioned eccentrically relative to the drive axis O3. Specifically, the counterweight 86 is located on one side opposite the eccentric pin 85 relative to the drive axis O3.

[0138] The drive shaft 83 is inserted into the insertion hole 73b, so that the counterweight 86 is located between the fixed block 73 and the rotor 82 in the motor chamber 75. Although not shown in detail, the counterweight 86 essentially has a fan-shaped plate form and extends outwards from the drive shaft 83 in the radial direction of the drive shaft 83. The shape of the counterweight 86 can be designed as is suitable.

[0139] The fixed screw 90 is fixed to and arranged within the compressor housing 72. The fixed screw 90 has a fixed screw end plate 90a, a fixed screw circumferential wall 90b, and a fixed screw body 90c. The fixed screw end plate 90a is located at the front end of the fixed screw 90 and is disc-shaped and perpendicular to the drive axis O3. The fixed screw end plate 90a has a second discharge recess 90d and a discharge port 90e.

[0140] The second discharge recess 90d is recessed to the rear. The fixed screw 90 is fixed to the compressor housing 72 such that the second discharge recess 90d faces the first discharge recess 72d. The first discharge recess 72d and the second discharge recess 90d work together to form a discharge chamber 91. The discharge chamber 91, in conjunction with the oil separation chamber 72c, extends through the discharge passage 72e. The discharge port 90e extends through the fixed screw end plate 90a in a front-to-back direction and is connected to the discharge chamber 91.

[0141] The dispensing diaphragm valve 57 and the holder 58 are fixed to the fixed screw end plate 90a by the fixing bolt 59. This design allows the dispensing diaphragm valve 57 to open and close the dispensing port 90e.

[0142] The fixed screw circumferential wall 90b is formed integrally with the fixed screw end plate 90a. The fixed screw circumferential wall 90b is connected to the outer circumference of the fixed screw end plate 90a and has a cylindrical shape, extending rearward toward the movable screw 110. The fixed screw circumferential wall 90b has a suction port 90f. The suction port 90f extends radially through the fixed screw circumferential wall 90b and opens toward the compressor housing 72. The fixed screw body 90c is located inside the fixed screw circumferential wall 90b and is formed integrally with the fixed screw end plate 90a. The fixed screw body 90c extends spirally toward the movable screw 110 in the direction of the drive axis O3.

[0143] The fixed screw 90 has an oil supply passage 44. The oil supply passage 44 is connected to the oil separation chamber 72c via the filter 77. The shape of the oil supply passage 44 can be designed as is suitable.

[0144] The movable screw 110 is arranged in the compressor housing 72 and is located between the fixed screw 90 and the fixed block 73. The movable screw 110 has a movable screw end plate 110a and a movable screw body 110b.

[0145] The movable worm end plate 110a is located at the rear end of the movable worm 110 and is disc-shaped, perpendicular to the drive axis O3. The movable worm end plate 110a supports the bushing 49 via a second radial bearing 46 such that the bushing 49 is rotatable. Consequently, the movable worm 110 is connected to the drive shaft 83 via the bushing 49 and the eccentric pin 85 at a position eccentric to the drive axis O3.

[0146] The movable worm end plate 110a is provided with the same number of rings 48 as the anti-rotation pins 47. Each of the rings 48 fits freely onto the tip of the anti-rotation pin 47. The anti-rotation pin 47 and the ring 48 work together to form an anti-rotation mechanism. Fig. 5 and Fig. The 6 represent one of the six rings 48. The number of anti-rotation pins 47 and the number of rings 48 of the anti-rotation mechanism can be changed as appropriate, as long as each of these is three or more.

[0147] The movable screw body 110b is formed integrally with the movable screw end plate 110a and extends towards the fixed screw end plate 90a. The movable screw body 110b has a feed hole 111 near its center, which opens at the front end of the movable screw body 110b and extends through the movable screw body 110b to the movable screw end plate 110a in a front-to-back direction.

[0148] The fixed screw 90 is assembled with the movable screw 110 in a front-to-back direction, so that the fixed screw 90 and the movable screw 110 interact to form a screw compression section 100a. A compression chamber 12a is formed between the fixed screw 90 and the movable screw 110 and is defined by the fixed screw end plate 90a, the fixed screw body 90c, the movable screw end plate 110a, and the movable screw body 110b. The compression chamber 12a changes its volume with the rotation of the movable screw 110. The compression chamber 12a allows the intake port 90f to be connected to the discharge port 90e.

[0149] A pressure plate 92 is arranged between the movable screw 110 and the fixed block 73. The pressure plate 92 is formed from a thin metal plate and is in contact with the movable screw 110 and the fixed block 73. The pressure plate 92 is designed to push the movable screw 110 forward, i.e., towards the fixed screw 90, by means of the restoring force generated when the pressure plate 92 is elastically deformed. The movable screw end plate 110a and the pressure plate 92 work together to form a counter-pressure chamber 93 in the hub 73a of the fixed block 73. The counter-pressure chamber 93 is connected to the feed hole 111.

[0150] The pressure accumulator 27 is a tubular component with a base and has an outer circumferential wall 27a and a rear wall 27b. The outer circumferential wall 27a has a cylindrical shape centered around the drive axis O3. The outer circumferential wall 27a has a first diameter section 271, a second diameter section 272, and a connecting section 273.

[0151] The first diameter section 271 forms the rear section of the outer circumferential wall 27a. The first diameter section 271 has a diameter larger than the diameter of the rotor 82. The second diameter section 272 is located in front of the first diameter section 271. The second diameter section 272 forms the front section of the outer circumferential wall 27a. The second diameter section 272 has a diameter smaller than the diameter of the first diameter section 271, and the diameter of the second diameter section 272 is approximately equal to the diameter of the rotor 82. The connecting section 273 is located between the first diameter section 271 and the second diameter section 272 and connects the front end of the first diameter section 271 and the rear end of the second diameter section 272.

[0152] The outer circumferential wall 27a, specifically the connecting section 273, has an outlet passage 27c. The outlet passage 27c extends through the connecting section 273 in the direction of the drive axis O3.

[0153] The rear wall 27b is located at the rear end of the pressure accumulator 27. The rear wall 27b is essentially circular and plate-shaped and is perpendicular to the drive axis O3. The outer circumferential edge of the rear wall 27b is connected to the rear end of the first diameter section 271. A through-hole 270 extends through the rear wall 27b in the direction of the drive axis O3 at the center of the rear wall 27b. The inner diameter of the through-hole 270 is slightly larger than the outer diameter of the support section 71c of the motor housing 71.

[0154] The pressure accumulator 27 is fixed to the rotor 82. Specifically, the front end of the second diameter section 272 of the pressure accumulator 27 is in contact with the second end plate 82c of the rotor 82. The pressure accumulator 27 is fixed to the second end plate 82c by the bolts 82d. That is, the pressure accumulator 27 is fixed to the first end plate 82b, the electromagnetic steel plates 82a, and the second end plate 82c by the bolts 82d in order to be fixed to the rotor 82, and is located behind the rotor 82. The pressure accumulator 27 can be fixed to the rotor 82 by bolts other than the bolts 82d or by other means.

[0155] Since the pressure accumulator 27 is fixed to the rotor 82 in this manner, a gas-liquid separation chamber 28 is defined within the pressure accumulator 27 by the outer circumferential wall 27a, the rear wall 27b, and the second end plate 82c. The gas-liquid separation chamber 28 is connected to the intake passages 84 and the outlet passage 27c. The outlet passage 27c is formed in the connecting section 273 of the outer circumferential wall 27a and is therefore located outside the intake passages 84 of the rotor 82 in the radial direction of the pressure accumulator 27. The gas-liquid separation chamber 28 is connected to the motor chamber 75 through the intake passages 84 and the outlet passage 27c.

[0156] The support section 71c is inserted through the through-hole 270 in the rear wall 27b of the pressure accumulator 27. The pressure accumulator 27 is housed in the motor chamber 75 and is rotatably supported in the gas-liquid separation chamber 28 by the support section 71c. Furthermore, the rear end section of the drive shaft 83 is located in the gas-liquid separation chamber 28. Consequently, the drive shaft 83 is rotatably supported in the gas-liquid separation chamber 28 by the support section 71c.

[0157] Compressor 3 is used for the air conditioning unit 200 (see Fig. 2 and Fig. 3) used. The refrigerant is drawn into the gas-liquid separation chamber 28 from the outside of the compressor 3 through the pipe H7 and the intake connection passage 76, as indicated by the dashed arrow in Fig. Figure 5 shows that in the compressor 3, the rotating shaft 83 rotates around the drive axis O3 with the rotation of the rotor 82. The movable screw 110 rotates, and the movable screw end plate 110a slides on the distal end of the fixed screw body 90c, and the fixed screw body 90c and the movable screw body 110b slide against each other. Rotation of the movable screw 110 is limited by the anti-rotation mechanism, and rotation of the movable screw 110 relative to the fixed screw 90 is permitted.

[0158] The pressure accumulator 27 is rotated around the drive axis O3 in the motor chamber 75 by the rotation of the rotor 82. Similar to the compressor 1 according to the first embodiment, this design of the compressor 3 ensures that the refrigerant drawn into the gas-liquid separation chamber 28 is suitably separated into the gaseous refrigerant and the liquid refrigerant under the influence of the centrifugal force of the rotating pressure accumulator 27.

[0159] The gaseous refrigerant in the gas-liquid separation chamber 28 is then drawn into the compression chamber 12a through the intake passages 84, the motor chamber 75, the connecting passage 73c and the intake port 90f (see the dashed arrows in Fig. 5) Accordingly, the compression chamber 12a reduces its volume with the rotation of the movable screw 110 and therefore compresses the refrigerant within it. The gaseous refrigerant, which has been highly compressed in the compression chamber 12a, is discharged from the discharge port 90e into the discharge chamber 91 and flows from the discharge chamber 91 to the oil separation chamber 72c through the discharge passage 72e. The highly compressed gaseous refrigerant is separated from the lubricating oil 18, while the gaseous refrigerant moves in a spiral pattern between the outer circumferential surface of the oil separation cylinder 70 and the inner circumferential surface of the oil separation chamber 72c, and the gaseous refrigerant then flows through the interior of the oil separation cylinder 70, the discharge connection port 72f and the pipe H1 and is discharged to the outside of the compressor 3.

[0160] The lubricating oil 18, which has been separated from the gaseous refrigerant, flows through the oil supply passage 44 via the filter 77 and is supplied to locations such as the motor chamber 75 and a sliding point between the fixed screw 90 and the movable screw 110.

[0161] A portion of the gaseous refrigerant, which has been highly compressed in the compression chamber 12a, is fed to the counter-pressure chamber 93 through the feed hole 111. Consequently, the pressure in the counter-pressure chamber 93 forces the movable screw 110 towards the compression chamber 12a over the pressure plate 92. The movable screw 110 is also forced towards the compression chamber 12a by the elastic force of the pressure plate 92. Thus, rotation of the movable screw 110 in the compressor 3 is prevented at an angle inclined with respect to the drive axis O3.

[0162] On the other hand, the liquid refrigerant is stored in the gas-liquid separation chamber 28. The lubricating oil 18 in the gas-liquid separation chamber 28 flows into the engine chamber 75 through the outlet passage 27c. The lubricating oil 18 lubricates the drive shaft 83 and the like and is drawn into the compression chamber 12a together with the gaseous refrigerant that has flowed through the intake passages 84. The outlet passage 27c is located outwards from the intake passages 84 in the radial direction of the pressure accumulator 27, so that the lubricating oil 18 can flow through the outlet passage 27c in the pressure accumulator in a suitable manner.

[0163] In compressor 3, the return passage 8a, in conjunction with the bottom of the motor chamber 75, passes through the first guide passage 62a and the second guide passage 62b. This design of compressor 3 allows the lubricating oil 18, which is stored at the bottom of the motor chamber 75, to flow into the gas-liquid separation chamber 28 through the first guide passage 62a, the second guide passage 62b, the return passage 8a, and the intake connection passage 76. Consequently, compressor 3 is also capable of exhibiting the same effects as compressor 1 according to the first embodiment.

[0164] In particular, in the compressor 3, the gaseous refrigerant flows in the gas-liquid separation chamber 28 into the connecting passage 73c through the intake passages 84 and the motor chamber 75. The intake passages 84, in conjunction with the gas-liquid separation chamber 28, are positioned inwards of the outlet passage 27c in the radial direction of the pressure accumulator 27. This design restricts the flow of the liquid refrigerant in the gas-liquid separation chamber 28 through the intake passages 84 and prevents it from remaining in the motor chamber 75. (Fourth example)

[0165] As in Fig. As shown in Figure 6, in the compressor 4 according to the fourth embodiment, the drive mechanism 80 has a drive shaft 94 instead of the drive shaft 83. In the compressor 4, the rear wall 71a of the motor housing 71 has a support section 71d.

[0166] In the same manner as the support section 71c of the compressor 3 according to the third embodiment, the support section 71d extends from the center of the rear wall 71a into the motor chamber 75. The support section 71d extends a shorter distance than the support section 71c and into the motor chamber 75. The support section 71d is not inserted into the through-hole 270 of the pressure accumulator 27. The support section 71d has a recess 711 at its front end, which is recessed towards the rear. In the same manner as the support section 71c, a sliding bearing 39 is arranged in the recess 711.

[0167] The support section 71d has an intake connection passage 95, in addition to the return passage 8a. The intake connection passage 95 opens at the rear wall 71a and extends forward from the rear wall 71a inside the support section 71d. The front end of the intake connection passage 95 is connected to the recess 711. The intake connection passage 95 is connected to the pipe H7. The intake connection passage 95 is also connected to the return passage 8a.

[0168] The drive shaft 94 is longer than the drive shaft 83 in the direction of the drive axis O3. Specifically, the drive shaft 94 projects further rearward from the rotor 82 than the drive shaft 83, and the drive shaft 94 is fixed to the rotor 82. The rear section of the drive shaft 94 is inserted through the through-hole 270 and projects rearward from the pressure accumulator 27.

[0169] The drive shaft 94 has a connecting channel 96. The connecting channel 96 has a first passage 96a and a second passage 96b. The first passage 96a opens at the rear end of the drive shaft 94 and extends forward inside the drive shaft 94. The second passage 96b is connected to the first passage 96a. The second passage 96b extends through the drive shaft 94 from the first passage 96a in the radial direction of the drive shaft 94 and opens at the outer circumferential surface of the drive shaft 94. The second passage 96b, i.e., the connecting channel 96, is connected to the gas-liquid separation chamber 28.

[0170] The drive shaft 94 is rotatably supported at its rear end by the support section 71d of the motor housing 71 via the sliding bearing 39, with the drive shaft 94 projecting rearward from the pressure accumulator 27. That is to say, in the compressor 4, the drive shaft 94 is rotatably supported externally by the support section 71d of the pressure accumulator 27. The pressure accumulator 27 is rotatably supported by the drive shaft 94.

[0171] The drive shaft 94 is rotatably supported by the support section 71d in such a way that the first passage 96a of the connecting channel 96 faces the intake connection passage 95 from the front. In the compressor 4, the intake connection passage 95 and the return passage 8a, in conjunction with the gas-liquid separation chamber 28, pass through the connecting channel 96.

[0172] In the same way as in the compressor 3 according to the third embodiment, the drive shaft 94 is formed integrally with the counterweight 86. The eccentric pin 85 is fixed to a front end face 94a of the drive shaft 94. Other configurations of the compressor 4 are the same as those of the compressor according to the third embodiment.

[0173] Compressor 4 is used for the air conditioning unit 200 (see Fig. 2 and Fig. 3) used. The refrigerant is drawn into the gas-liquid separation chamber 28 from the outside of the compressor 4 through the pipe H7, the intake connection passage 95 and the connecting channel 96, as indicated by the dashed arrow in Fig.6 is characterized, and the gaseous refrigerant and the liquid refrigerant are separated in the gas-liquid separation chamber 28. Other operations of compressor 4 are the same as those of compressor 3 according to the third embodiment.

[0174] Although the present invention has been described above based on the first to fourth embodiments, the present invention is not limited to the first to fourth embodiments described above and can be modified within the core of the present invention as is appropriate.

[0175] For example, in compressor 1 according to the first embodiment, both the cover body 35 and the output screw end plate 41 can have the intake passage 35a, and both the cover body 35 and the output screw end plate 41 can have the supply passage 35b. The same applies to compressor 2 according to the second embodiment.

[0176] In the compressor 1 according to the first embodiment, the output screw 40 is housed within the drive screw 30 and assembled with it. However, the present invention is not limited to this configuration, and the output screw 40 can be arranged on the outside of the drive screw 30 and assembled with it. In this configuration, the output screw end plate 41 can have the intake passage 35a and the feed passage 35b and can be fixed to the pressure accumulator 15. The same applies to the compressor 2 according to the second embodiment.

[0177] In the compressor 1 according to the first embodiment, the drive screw 30 can be connected to the rotor 11 via a shaft for power transmission, such that the drive screw 30 and the pressure accumulator 15 are spaced apart from the rotor 11 in the direction of the drive axis O1. The same applies to the compressor 2 according to the second embodiment.

[0178] In compressors 1 and 2 according to the first and second embodiments, the output mechanism 20 has the anti-rotation pins 21 and the rings 22. However, the present invention is not limited thereto, and the output mechanism 20 can be designed by a pin-ring-pin mechanism in which two pins slide on the inner circumferential surface of a free ring, a pin-and-pin mechanism in which the outer circumferential surfaces of two pins slide against each other, a mechanism that uses an Oldham shaft coupling, or the like. The same applies to the anti-rotation mechanisms in compressors 3 and 4 according to the third and fourth embodiments. COMMERCIAL APPLICABILITY

[0179] The present invention is applicable to the air conditioning system for the vehicle or the like. REFERENCE MARK LIST 1 to 4 compressors (scroll compressors) 6, 7 Housing 8, 8a Backflow passage 10.80 Drive mechanism 11, 82 Rotor 12, 12a Compression chamber 15, 25, 27 Pressure accumulators 17, 81 Stator 20 Output mechanism 27c Outlet passage 30 Drive screw (first screw) 35a, 84 Intake passage 35b, 35c Inlet 40 discharge screw (second screw) 83, 94 Drive shaft 90 fixed snail (first snail) 110 movable worms (second worm) O1, O3 drive axle O2 output shaft QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 04-076287

[0005]

Claims

[1] Scroll compressor comprising: a housing; a drive mechanism; a first screw; and a second screw, wherein the drive mechanism, the first worm and the second worm are housed in the casing, and the first screw and the second screw form a compression chamber for compressing a refrigerant, wherein The drive mechanism has the following: a stator that is fixed to the housing; and a rotor that has a cylindrical shape and is rotatable within the stator. a pressure accumulator is housed in the casing the housing has an intake passage through which the refrigerant, which contains a lubricating oil, is drawn into the pressure accumulator from an outside of the housing, The refrigerant, which has been drawn through the intake connection passage, is separated by the pressure accumulator into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil. The gaseous refrigerant in the pressure accumulator is drawn into the compression chamber through an intake passage, and the pressure accumulator is fixed to the first screw, the second screw or the rotor in such a way that the pressure accumulator can be rotated in the housing. [2] Scroll compressor according to claim 1, wherein the housing has a return passage through which the lubricating oil in the housing flows into the pressure accumulator. [3] Scroll compressor according to claim 1 or 2, wherein the first worm is driven by the drive mechanism to rotate around a drive axis, the second screw is eccentric to the first screw and is driven by the first screw and an output mechanism to rotate around an output axis, at least one of the first screw and the second screw has an intake passage and a supply passage through which the lubricating oil in the pressure accumulator is supplied to the compression chamber, and The feed passage is located outside the intake passage in a radial direction of the first screw and a radial direction of the second screw and is connected to the pressure accumulator. [4] Scroll compressor according to claim 3, wherein the pressure accumulator is fixed to the first screw and an inner circumferential surface of the rotor, and the first screw is not in contact with the rotor. [5] Scroll compressor according to claim 3, wherein the first screw is fixed to an inner circumferential surface of the rotor, and The pressure accumulator is fixed to the first screw and is not in contact with the rotor. [6] Scroll compressor according to claim 1 or 2, wherein The drive mechanism also has a drive shaft that is fixed to the rotor and rotatable within the housing. the first snail is fixed to the shell, the second worm is connected to the drive shaft and rotates relative to the first worm with a rotation of the drive shaft, the pressure accumulator is fixed to the rotor the rotor has the intake passage, and The pressure accumulator has an outlet passage located outside the intake passage in a radial direction of the pressure accumulator, through which the lubricating oil in the pressure accumulator flows into the compression chamber.

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