Rotating screw compressor

Abstract

A rotating screw compressor (1) has a housing (6), a drive mechanism (10), a drive screw (30), a driven screw (40), and a driven mechanism (20). An intake chamber (65) is formed in the housing (6), into which a refrigerant containing lubricating oil (18) is drawn from outside the housing (6). A reservoir (15) is located in the intake chamber (65). The reservoir (15) is connected to the intake chamber (65), draws the refrigerant into the intake chamber (65), and separates the refrigerant into a gaseous refrigerant and a liquid refrigerant. The reservoir (15) is attached to the driven screw (30) in such a way that it can rotate within the intake chamber (65). In the driven screw (30) an inlet passage (35a) is formed which is connected to the interior of the storage unit (15) and makes it possible to draw the gaseous refrigerant in the storage unit (15) into a compression chamber (12).

Description

[0001] The present invention relates to a moving screw compressor. STATE OF THE ART

[0002] Patent literature 1 discloses a known mobile screw compressor (hereinafter referred to simply as the compressor). The compressor has a housing, a drive mechanism, a drive screw, a driven screw, and a drive mechanism. The housing has a main frame that defines a screw chamber and a low-pressure chamber within the housing. The drive screw, the driven screw, and the driven 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 housing has an intake pipe through which the low-pressure chamber is connected to the outside of the housing.

[0003] The drive screw is positioned opposite the driven screw in the screw chamber. Together, the drive screw and the driven screw form a compression chamber between them. The drive screw has a drive shaft. The drive shaft is rotatably mounted to the main frame, extends into the low-pressure chamber, and is attached to the drive mechanism. The driven mechanism is located between the drive screw and the driven screw.

[0004] In this compressor, the drive screw is rotated around the drive axis by the drive mechanism, and the driven screw is rotated around the driven axis by the drive screw and the driven mechanism. A refrigerant is drawn from outside the casing through the intake line into the low-pressure chamber and then drawn through the intake port into the screw chamber. In this compressor, the volume of the compression chamber changes with the rotation of the drive screw and the rotation of the driven 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 no. H04 - 076 287 SUMMARY OF THE INVENTION Technical Problem

[0006] This type of compressor can be used in an air conditioning system that includes a heat exchanger and similar components. In such a system, there is a risk that liquid refrigerant in the heat exchanger, along with gaseous refrigerant in its vapor phase, could be drawn into the casing when the air conditioner switches from cooling to heating mode, for example. If this liquid refrigerant is drawn into the compression chamber and compressed there, the drive screw and the driven helix can be damaged, reducing the compressor's reliability.

[0007] Accordingly, consideration is being given to providing a storage unit in this compressor 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 accumulator due to the separation of gas and liquid, the liquid refrigerant can be transported upwards within the accumulator by the gaseous refrigerant drawn into it. Consequently, the separation of gas and liquid in the accumulator may be insufficient, and some of the liquid refrigerant in the accumulator may be drawn into the low-pressure chamber and, consequently, into the compression chamber along with the gaseous refrigerant.

[0009] The present invention, which was developed taking into account the above-mentioned problem, aims to provide a mobile screw compressor with excellent reliability. Solution to the problem

[0010] A self-propelled screw compressor according to the present invention has: a housing; a drive mechanism; a drive screw; a driven screw; and a driven mechanism, wherein the housing has an intake chamber in which the drive screw and the driven screw are housed and into which a refrigerant containing lubricating oil is drawn from outside the housing, the drive worm is configured to be set in rotation by the drive mechanism around a drive axis, The driven screw is arranged and configured eccentrically to the drive screw, to be set in rotation about a drive axis by the drive screw and the drive mechanism, and the drive screw and the driven screw form a compression chamber for compressing the refrigerant, wherein a storage unit is housed in the intake chamber, wherein the storage unit is connected to the intake chamber, the storage unit receives the refrigerant drawn in from the intake chamber and makes it possible to separate the refrigerant into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil, the storage unit is attached to the drive screw or the driven screw and is rotatable in the intake chamber, and at least one of the drive screw and the driven screw has an intake passage that is connected to the storage tank and through which the gaseous refrigerant in the storage tank is drawn into the compression chamber.

[0011] In the rotating screw compressor according to the present invention, in addition to the drive screw and the driven screw, the accumulator is housed in the intake chamber of the casing. The refrigerant is drawn into the intake chamber from outside the casing. The refrigerant contains lubricating oil. The refrigerant in the intake chamber is drawn into the accumulator. Accordingly, the refrigerant in the compressor is not drawn directly into the accumulator from outside the casing.

[0012] This means that in the compressor, the refrigerant is drawn from outside the casing into the intake chamber, where it is first separated into gaseous and liquid refrigerant. The refrigerant is then drawn from the intake chamber into the reservoir, where it is further separated into gaseous and liquid refrigerant. This initial separation of the refrigerant into gas and liquid in the intake chamber results in a lower probability of the refrigerant being liquid when it enters the reservoir, compared to a configuration where the refrigerant is drawn directly from outside the casing into the reservoir and only separated into gaseous and liquid refrigerant within the reservoir itself.

[0013] In the compressor, the accumulator is attached to the drive screw or the driven screw and rotates within the intake chamber. This causes the refrigerant drawn into the accumulator to be separated into gaseous and liquid refrigerant by the centrifugal force of the rotating accumulator. The gaseous refrigerant in the accumulator is drawn through the intake port into the compression chamber and compressed there. Due to centrifugal force, the liquid refrigerant, separated from the gaseous refrigerant, tends to remain on the radially outer side of the accumulator, i.e., on the radially outer side of the drive screw and the driven screw.

[0014] This compressor configuration prevents the liquid refrigerant in the storage tank from being drawn into the compression chamber, even if a large quantity of liquid refrigerant is present in the storage tank. Consequently, it is less likely that the compressor will compress the liquid refrigerant in the compression chamber.

[0015] The gaseous refrigerant drawn into the compression chamber may contain some lubricating oil, thus lubricating the chamber. Consequently, wear on the drive screw and the driven screw within the compressor is less likely.

[0016] Therefore, the moving screw compressor according to the present invention exhibits excellent reliability.

[0017] The housing can have a support section that extends into the intake chamber and mounts the accumulator so that it can rotate. The support section preferably has a return passage through which the lubricating oil in the intake chamber flows into the accumulator.

[0018] This allows the lubricating oil in the intake chamber to flow appropriately into the reservoir via the return passage. In this way, the lubricating oil in the intake chamber can be returned to the compression chamber via the reservoir, thus lubricating the compression chamber appropriately.

[0019] At least one of the drive screw and the driven screw can have a supply passage through which the lubricating oil is supplied to the reservoir of the compression chamber. The supply passage is preferably located outside the intake passage in the radial direction of the drive screw and in the radial direction of the driven screw and is connected to the reservoir.

[0020] The lubricating oil in the accumulator likely collects on the radially outer side of the drive and driven screws under the influence of the centrifugal force of the rotating accumulator. In this context, at least one of the drive and driven screws of the compressor has a passage, and this passage is located radially outside the intake passage of the drive and driven screws and is connected to the accumulator. This configuration allows the lubricating oil in the accumulator to be supplied to the compression chamber via this passage. Accordingly, the compression chamber is lubricated by the lubricating oil.

[0021] In the compressor, some of the liquid refrigerant in the reservoir inevitably flows through the feed passage along with the lubricating oil. However, the liquid refrigerant is evaporated by the heat generated by the drive screw and the driven screw as it flows towards the compression chamber. This prevents the liquid refrigerant in the reservoir from being drawn into the compression chamber through the feed passage.

[0022] In the compressor, the intake passage is located radially in the direction of the drive screw and the driven screw within the supply passage, and this configuration appropriately prevents the liquid refrigerant in the storage tank from being drawn into the compression chamber through the intake passage.

[0023] The drive mechanism can comprise the following: a stator attached to the housing and located in the intake chamber; and a cylindrical rotor rotatably mounted within the stator. The accumulator is preferably attached to the drive worm and arranged inside the rotor.

[0024] By attaching the compressor's accumulator to the drive screw and arranging the accumulator inside the rotor, the need to extend the housing in the direction of the drive axis is reduced, compared to a configuration in which the accumulator is attached to the drive screw and located outside the rotor, for example.

[0025] The drive mechanism can have: a stator housed in the intake chamber and attached to the casing; and a cylindrical rotor rotatably mounted within the rotor. The drive screw can be located within the rotor. The storage device is preferably attached to the drive screw.

[0026] This configuration eliminates the need to position the accumulator inside the rotor, thereby increasing flexibility in the accumulator's shape. This easily allows for an increase in the accumulator's diameter, facilitating the centrifugal separation of the liquid refrigerant and lubricating oil in the compressor. Advantageous effects of the invention

[0027] The moving screw compressor according to the present invention exhibits excellent reliability. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a cross-sectional view of a moving screw compressor according to a first embodiment. Fig. Figure 2 is a schematic representation of an air conditioning system which has the rotating screw compressor according to the first embodiment, and which shows the operation of the air conditioning system in cooling mode. Fig. Figure 3 is a schematic representation of the air conditioning system which has the co-rotating screw compressor, according to the first embodiment, which shows the air conditioning system in heating mode. Fig. Figure 4 is a cross-sectional view of a co-rotating screw compressor according to a second embodiment. DESCRIPTION OF THE EXECUTION FORMS

[0028] A first embodiment and a second embodiment of the present invention are described in detail below with reference to the accompanying drawings. A compressor 1 according to the first embodiment and a compressor 2 according to the second embodiment are installed on a vehicle (not shown). (First embodiment)

[0029] Fig. Figure 1 shows the compressor 1 according to the first embodiment with a housing 6, an electric motor 10, a drive screw 30, a driven screw 40, a driven mechanism 20 and a storage unit 15. The electric motor 10 serves, for example, as the drive mechanism of the present invention.

[0030] In the present embodiment, the forward / reverse direction and the upward / downward direction of compressors 1, 2 are indicated by solid arrows in the Fig. 1 and Fig. 4 is defined. The forward / reverse direction and the upward / downward direction are perpendicular to each other. In the embodiments, the compressors 1, 2 are installed on the vehicle such that the undersides of the compressors 1, 2 correspond to the underside of the vehicle. It should be noted that the directions are merely an example for the sake of clarity and the position of the individual compressors 1, 2 can be changed accordingly depending on the vehicle on which the individual compressors 1, 2 are installed.

[0031] As from Fig. As can be seen 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 plastic. The attachment 62 may also be made of an aluminum alloy.

[0032] The housing body 60 is a tubular element with a base and has an outer wall 60a and a rear wall 60b. The outer wall 60a is cylindrical and centered on a drive axis O1. The drive axis O1 runs parallel to the forward / reverse direction. The outer wall 60a has an intake connection 69. The intake connection 69 extends radially through the outer wall 60a of the housing body 60. The intake connection 69 is connected to a pipe H7. The intake connection 69 is connected via the pipe H7 to the outside of the housing 6, i.e., the outside of the compressor 1.

[0033] The rear wall 60b is located at the rear end of the housing body 60. The rear wall 60b has a substantially circular plate shape and is perpendicular to the drive axis O1. The outer edge of the rear wall 60b is connected to the rear end of the outer wall 60a. The rear wall 60b has a first support section 64 at the center point of the inner surface of the rear wall 60b. The first support section 64 serves, for example, as a support section of the present invention. The first support section 64 has a substantially circular, solid cylindrical shape, which is centered around the drive axis O1 at the center point of the inner surface of the rear wall 60b, and extends from there forward into a suction chamber 65, which will be described later.

[0034] The first support section 64 has a pin hole 4. The pin hole 4 is formed on the front surface of the first support section 64 and extends linearly and rearward within the first support section 64. The pin hole 4 does not extend through the first support section 64 in the forward / backward direction.

[0035] The first support section 64 has a return passage 8. The return passage 8 has a main return passage 8a, a first radial passage 8b, and a second radial passage 8c. The main return passage 8a opens at the rear wall 60b and extends forward from the rear wall 60b in the direction of the drive axis O1 within the first support section 64. The main return passage 8a is spaced from the pin hole 4 in the forward / backward direction and is not in contact with the pin hole 4. The opening of the return passage 8a at the rear wall 60b is closed by a sealing element 81, and the main return passage 8a is not in contact with the outside of the housing 6.

[0036] The first radial passage 8b is located at the rear end of the first support section 64 and is connected to the main return passage 8a. The first radial passage 8b extends through the first support section 64 from the main return passage 8a in the radial direction of the first support section 64 and opens at the outer circumferential surface of the first support section 64. Within the first support section 64, the second radial passage 8c is located upstream of the first radial passage 8b and essentially at the midpoint of the first support section 64 in the forward / backward direction. The second radial passage 8c is connected to the main return passage 8a. Similar to the first radial passage 8b, the second radial passage 8c extends through the first support section 64 from the main return passage 8a in the radial direction of the first support section 64 and opens at the outer circumferential surface of the first support section 64.

[0037] The housing cover 61 is arranged in front of the housing body 60. The housing cover 61 has a substantially circular plate shape and is perpendicular to the drive axis O1. The housing cover 61 is fastened to the housing body 60 with screws (not shown), 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. Accordingly, the housing body 60 is closed at the front by the housing cover 61. The housing body 60 therefore has the suction chamber 65 inside the housing body 60.

[0038] The housing cover 61 has a second support section 67 in the center of its inner surface. The second support section 67 is cylindrical, centered around the drive axis O1, and extends rearward from the center of the housing cover's inner surface. An outer ring of a needle bearing 14 is fitted into the second support section 67.

[0039] The housing cover 61 has an outlet port 68. The outlet 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 outlet port 68 is connected to an outlet chamber 13, which will be described later. The outlet port 68 is connected to a pipe H1. The outlet port 68 is connected to the outside of the compressor 1 via the pipe H1.

[0040] The intake chamber 65 is connected to the intake connection port 69. This configuration allows a refrigerant from outside the compressor 1 to be drawn into the intake chamber 65 through the pipe H7, which is connected to the intake connection port 69.

[0041] The attachment 62 is located in the intake chamber 65 and is mounted on the rear wall 60b of the housing body 60. The attachment 62 is plate-shaped and extends perpendicular to the drive axis O1. The attachment 62 has a first guide passage 62a and a second guide passage 62b.

[0042] The first guide passage 62a is recessed into the rear 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 radially along the housing body 60. The first passage 62a communicates with the first radial passage 8b at its upper end.

[0043] The second guide passage 62b is formed in the lower section of the attachment 62. The second guide passage 62b opens at its front end onto the surface of the attachment 62 facing the suction chamber 65 and is connected at its rear end to the first guide passage 62a. The first radial passage 8b, i.e., the return passage 8, communicates with the bottom of the suction chamber 65 via the first guide passage 62a and the second guide passage 62b. The attachment 62 need not necessarily be mounted on the housing body 60, and the first radial passage 8b can be in direct communication with the suction chamber 65.

[0044] The electric motor 10 is housed in the intake chamber 65. The intake chamber 65 serves as the motor chamber in which the electric motor 10 is located. The electric motor 10 has a stator 17 and a rotor 11. The stator 17 has a cylindrical shape centered around the drive axis O1 and has a winding wire 17a. The stator 17 is fitted onto the inner surface of the outer circumferential wall 60a, so that the stator 17 is attached to the housing body 60.

[0045] 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 consists of a plurality of permanent magnets corresponding to the stator 17, electromagnetic steel sheets for mounting the permanent magnets, and the like.

[0046] The drive screw 30 is made of an aluminum alloy. The drive screw 30 is housed in the intake 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.

[0047] The drive worm end plate 31 is essentially disc-shaped and is perpendicular to the drive axis O1 and the 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 forward / reverse direction.

[0048] The drive worm end plate 31 has opposing surfaces: a front surface 311 facing the housing cover 61, and a rear surface 312 located in the intake chamber 65. A first projection 34 extends from the center of the front surface 311 towards the housing cover 61. The first projection 34 has a cylindrical shape, the center of which lies on the drive shaft O1.

[0049] The drive worm end plate 31 has an outlet 38. The outlet 38 is formed in the first projection 34 of the drive worm end plate 31 and extends through the drive worm end plate 31 in the forward / reverse direction.

[0050] In the first hub 34, an exhaust tongue valve 57 and a bracket 58 with a fastening screw 59 are attached to the drive worm end plate 31. The exhaust tongue valve 57 opens and closes the exhaust port 38, and the bracket 58 adjusts the opening degree of the exhaust tongue valve 57.

[0051] The drive worm circumferential wall 32 has a cylindrical shape, centered around the drive axis O1 at its midpoint, and extends parallel to the drive axis O1 and the output axis O2. The drive worm circumferential wall 32 is integrated with the outer 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.

[0052] The drive worm body 33 is arranged within the drive worm circumferential wall 32. The drive worm body 33 is formed integrally with the drive worm end plate 31 and extends from the rear side 312 of the drive worm end plate 31 rearward toward the driven worm 40 and parallel to the drive axis O1 and the output axis O2. Although not shown in detail, the drive worm body 33 has a helical shape centered around the midpoint of the drive worm end plate 31 and extending radially outward from the center of the helical shape. The drive worm body 33 is connected to the inner surface of the drive worm circumferential wall 32 at its outer edge.

[0053] 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 face 351 and a back face 352. The front face 351 is oriented in the forward / reverse direction of the back face 312 of the drive worm end plate 31. The back face 352 is opposite the front face 351.

[0054] The cover body 35 has a second projection 36, an intake passage 35a, and a supply passage 35b. The second projection 36 is integrally formed with the cover body 35 at its center and extends from the rear side 352 to the rear. The second projection 36 has an insertion hole 350. The insertion hole 350 extends through the second projection 36 and the cover body 35 in the direction of the drive axis O1. The second projection 36 has a cylindrical shape, aligned around the drive axis O1 at its center point. A sliding bearing 51 is arranged in the insertion hole 350. Instead of the sliding bearing 51, a ball bearing or the like may also be arranged in the insertion hole 350.

[0055] The intake passage 35a is formed by the cover body 35 in a forward / reverse direction. The supply passage 35b is located outside the intake passage 35a in the radial direction of the cover body 35. The supply passage 35b is formed by the cover body 35 in a forward / reverse direction. 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 351 are located in the radial direction of the cover body 35 outside the opening of the intake passage 35a and the opening of the supply passage 35b on the rear 352. This means that the intake passage 35a and the supply passage 35b extend in the radial direction of the cover body 35 from the rear 352 to the front 351.

[0056] A plurality of rings 22 are attached to the cover body 35 at positions radially outside the second projection 36. The rings 22 are arranged at equal intervals in the circumferential direction of the cover body 35, point forward, and surround the second projection 36 and the insertion hole 350. In the present embodiment, the number of rings 22 is six. Fig. It is evident from Figure 1 that two of the six rings 22 are present. The same applies to Fig. 4.

[0057] The in from Fig. The driven screw 40 shown is made of an aluminum alloy. The driven screw 40 is housed in the suction chamber 65, more precisely inside the drive screw 30. The driven screw 40 has an end plate 41 and a body 43.

[0058] The end plate 41 of the driven screw is essentially disc-shaped and is perpendicular to the drive axis O1 and the driven axis O2. The end plate 41 of the driven screw has a front surface 411 and a back surface 412. Surface 411 faces the back surface 312 of the drive screw end plate 31 in the drive screw 30. The back surface 412 is opposite surface 411 and faces the surface 351 of the cover body 35.

[0059] The end plate 41 of the driven screw has a receiving section 41a. The receiving section 41a has a shape centered around the output axis O2 and is cylindrically recessed forward from the rear surface 412 of the end plate 41 of the driven screw. A bushing 53 is arranged in the receiving section 41a. The bushing 53 can be mounted in the receiving section 41a via a bearing, for example, a plain bearing or a ball bearing.

[0060] A driven pin 55 is inserted into the bushing 53. The driven pin 55 is inserted into the bushing 53 at its center point, i.e., at a position eccentric to the drive axis O2. The driven pin 55 is made of steel and has a solid cylindrical shape. The driven pin 55 projects rearward from the bushing 53, i.e., from the driven worm end plate 41.

[0061] A plurality of anti-rotation pins 21 are attached to the end plate 41 of the driven worm at positions radially outside the receiving section 41a, and the anti-rotation pins 21 project rearward from the rear side 412. In particular, each of the anti-rotation pins 21 is attached to a position outside the receiving section 41a and opposite the ring 22. In the end plate 41 of the driven worm, the anti-rotation pins 21 are arranged at equal intervals circumferentially around the end plate 41 of the driven worm and surround the receiving 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. Figure 4 shows two of the six anti-rotation pins 21.

[0062] As from Fig. As can be seen in Figure 1, the body 43 of the driven worm is formed integrally with the end plate 41 of the driven worm and extends from the front face 411 of the end plate 41 of the driven worm forwards towards the end plate 31 of the drive worm and parallel to the drive axis O1 and the output axis O2. Although not shown in detail, the body 43 of the driven worm has a helical shape centered around the midpoint of the end plate 41 of the driven worm and extending outwards from the midpoint of the helical shape.

[0063] The drive 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 drive mechanism 20 can be changed accordingly, as long as at least three are present in each case.

[0064] The storage unit 15 is a tubular element with a base and has an outer wall 15a and a rear wall 15b. The outer wall 15a has a cylindrical shape centered around the drive axis O1. The outer diameter of the outer wall 15a corresponds essentially to the inner diameter of the rotor 11. The rear wall 15b is located at the rear end of the storage unit 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 wall 15a.

[0065] A through-hole 150 is formed through the rear wall 15b at its center point, extending towards the drive axis O1. 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. The rear wall 15b has an intake flow path 151 located radially outside the through-hole 150. The intake flow path 151 has a diameter smaller than the diameter of the through-hole 150 and extends through the rear wall 15b towards the drive axis O1.

[0066] In the compressor 1, the front 351 of the cover body 35 faces the rear 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 screws 50a. Accordingly, the drive screw end plate 31, the drive screw circumferential wall 32, and the cover body 35 are formed integrally.

[0067] In the compressor 1, the driven screw 40 is housed within the drive screw 30, and the drive screw body 33 engages with the driven screw 43. Each of the anti-rotation pins 21 is inserted into the ring 22. In this way, the drive screw 30 is assembled with the driven screw 40 in the forward / reverse direction, so that the drive screw 30 and the driven screw 40 interact to form a screw compression unit 100. Specifically, the drive screw body 33 engages with the body 43 of the driven screw, the anti-rotation pin 21 is inserted into the ring 22, and the drive screw end plate 31 and the drive screw circumferential wall 32 of the drive screw 30 are connected to the cover body 35 by the screws 50a.

[0068] By assembling the drive screw 30 with the driven screw 40, an intake chamber 30a can be formed by the drive screw 30 and the driven screw 40. That is, the drive screw body 33 and the body 43 of the driven screw are located within the intake chamber 30a. The intake chamber 30a is separated from the intake chamber 65 by the drive screw end plate 31, the drive screw circumferential wall 32, and the cover body 35.

[0069] In the drive screw 30, the cover body 35 is located behind the drive screw body 33, the body 43 of the driven screw, and the end plate 41 of the driven screw, in the direction of the drive axis O1. Accordingly, in the drive screw housing 30, i.e., in the screw compression section 100, the cover body 35 is located furthest back in the direction of the drive axis O1.

[0070] In the compressor 1, the storage tank 15 is attached to the drive screw housing 30. Specifically, the outer wall 15a of the storage tank 15 faces the cover body 35, and the front end of the outer wall 15a is in contact with the rear side 352 of the cover body 35. The storage tank 15 is fastened to the cover body 35 with screws 50b. Accordingly, the storage tank 15 and the drive screw 30 are formed as a single unit.

[0071] Since the storage tank 15 is attached to the drive screw 30 in this way, a separation chamber 16 for gas and liquid is formed in the storage tank 15 by the outer wall 15a and the rear wall 15b of the storage tank 15 as well as the cover body 35. The separation chamber 16 for gas and liquid is connected to the intake chamber 30a via the intake passage 35a and the supply passage 35b.

[0072] In the storage unit 15, the outer wall 15a is inserted into the rotor 11 and attached to the inner surface of the rotor 11. This means that the storage unit 15 is located inside the rotor 11 and is attached to both the drive screw 30 and the rotor 11. Accordingly, the storage unit 15 is rotatable together with the rotor 11, and the drive screw 30 is also rotatable with the rotation of the storage unit 15.

[0073] The first support section 64 of the housing body 60 is inserted through the through-hole 150 in the rear wall 15b of the storage tank 15. The storage tank 15 is received in the intake chamber 65 and is rotatably held in the gas-liquid separation chamber 16 by the first support section 64. The gas-liquid separation chamber 16 is connected to the intake chamber 65 via the intake flow path 151. The gas-liquid separation chamber 16 is connected to the return passage 8.

[0074] The front part of the first support section 64 is inserted into the sliding bearing 51, i.e., the second projection 36 of the drive worm 30. Accordingly, the cover body 35 is rotatably held by the first support section 64 via the sliding bearing 51.

[0075] 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 mounted via the needle bearing 14 on the second support section 67 of the housing cover 61. In this way, the first hub 34 is held by the second support section 67, so that the outlet 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.

[0076] Accordingly, the drive worm 30 is held 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 about the drive axis O1.

[0077] In the driven worm 40, the drive pin 55 is inserted into the pin hole 4 of the first support section 64. Accordingly, the driven worm 40 is rotatably held by the first support section 64, so that the driven worm 40 is rotated about the output axis O2 by the driven pin 55. That is to say, in contrast to the drive worm 30, the driven worm 40 is held only by the first support section 64 of the housing 6, so that the driven worm 40 can rotate about the output axis O2.

[0078] The output axis O2 is eccentric to the drive axis O1. The driven worm 40 is held by the housing 6 in such a way that the driven worm 40 is rotatable about the output axis O2 and is eccentric to the drive worm 30 and is received in it.

[0079] Compressor 1 is used for a [unclear] in the Fig. 2 and Fig. The air conditioning unit 200 is shown in Figure 3. The air conditioning unit 200 has a compressor 1 and further comprises: a condenser 101, an external heat exchanger 102, an evaporator 103, a receiver 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 the pipes H1 to H10. The first flow diverter valve 105 and the second flow diverter valve 106 are, in particular, three-way valves.

[0080] The outlet port 68 of compressor 1 is connected via pipe H1 to an inlet 101a of condenser 101. An outlet 101b of condenser 101 is connected via pipe H2 to the first flow diverter valve 105. The first flow diverter valve 105 is connected via pipe H3 to an inlet 102a of external heat exchanger 102. An outlet 102b of external heat exchanger 102 is connected via pipe H4 to the second flow diverter valve 106.

[0081] The second flow diverter valve 106 is connected to the collector 104 via pipe H5. The collector 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 suction port 69 of the compressor 1 via pipe H7.

[0082] 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.

[0083] The first expansion valve 107 is provided in pipe H3. The second expansion valve 108 is provided in pipe H6. The on / off valve 109 is provided in pipe H9. Although not apparent, the compressor 1, the first flow diverter valve 105 and the second flow diverter valve 106, the first expansion valve 107 and the second expansion valve 108, and the on / off valve 109 are connected to a control device (not shown) installed on the vehicle.

[0084] When the air conditioner 200 is in cooling mode, the first flow diverter valve 105 connects, as shown in the diagram. Fig. As can be seen in Figure 2, pipe H2 and pipe H3 are connected, and pipes H2 and H3 are separated from pipe H8. The second flow diverter valve 106 connects pipe H4 and pipe H5 and separates 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 adjusted, and the on / off valve 109 is closed. During cooling operation, the opening degree of the first expansion valve 107 is almost maximum.

[0085] Accordingly, in the air conditioning system 200, the refrigerant discharged from compressor 1 flows in this order through pipe H1, condenser 101, pipe H2, and pipe H3 into the external heat exchanger 102. 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, now warmed in the external heat exchanger 102, flows from the external heat exchanger 102 through pipe H4, pipe H5, receiver 104, and pipe H6, in this order, into the evaporator 103. At this point, the opening of the second expansion valve 108 is adjusted accordingly to regulate the pressure of the refrigerant flowing from pipe H6 into the evaporator 103.

[0086] 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 interior, thus cooling the interior. The refrigerant, from which the heat is transferred in the evaporator 103, flows from the evaporator 103 through pipe H7 into the compressor 1. During cooling operation, the air surrounding the condenser 101 is warmed by heat transfer from the refrigerant flowing through the condenser 101. However, the warmed air is not supplied to the vehicle interior.

[0087] When the air conditioner 200 is in heating mode, the first flow diverter valve 105 connects, as shown in the diagram. Fig. Figure 3 shows pipe H2 and pipe H8, and separates pipes H2 and H8 from pipe H3. The second flow diverter valve 106 connects pipe H4 and pipe H10 and separates pipes H4 and H10 from pipe H5. The opening degree of the first expansion valve 107 is adjusted, and the on / off valve 109 is opened.

[0088] Accordingly, in the air conditioning system 200, the refrigerant is expelled from the compressor 1 and flows through the pipe H1 into the condenser 101. 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's interior, thus warming the interior.

[0089] The refrigerant, from which heat is transferred in condenser 101, flows from condenser 101 through pipe H2, pipe H8, pipe H6, receiver 104, pipe H5, pipe H9, and pipe H3, in that order, into the external heat exchanger 102. At this point, the opening of the first expansion valve 107 is adjusted accordingly to match 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 the transfer of heat from the air outside the vehicle. The refrigerant heated in the external heat exchanger 102 then flows from the external heat exchanger 102, in that order, through pipe H4, pipe H10, and pipe H7 into compressor 1.

[0090] In particular, during the operation of compressor 1, as shown from Fig. As can be seen in Figure 1, the electric motor 10 is actuated in such a way that the rotor 11 rotates, causing the accumulator 15 to rotate around the drive axis O1 in the intake chamber 65. The drive screw 30 is also rotated by the rotation of the accumulator 15 around the drive axis O1 in the intake chamber 65. That is to say, 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 accumulator 15.

[0091] In the driven mechanism 20, each of the anti-rotation pins 21 slides on the inner circumferential surface of the ring 22 with the rotations of the storage unit 15 and the drive worm 30, allowing the ring 22 to rotate relative to the anti-rotation pin 21 about the axis of the anti-rotation pin 21. In this way, the drive mechanism 20 transmits the torque of the drive worm 30 to the driven worm 40.

[0092] Accordingly, the driven screw 40 is driven by the drive screw 30 and the drive mechanism 20 to rotate around the drive axis O2. The drive mechanism 20 prevents the driven screw 40 from rotating around its own axis. Therefore, the driven screw 40 orbits the drive screw 30 around the drive axis O2. The drive screw 33 and the driven screw 43 rotate in the intake chamber 30a, so that the drive screw 33 and the driven screw 43 come into contact. The drive screw 33 and the driven screw 43 thus form a compression chamber 12 between them.

[0093] The refrigerant is moved by the rotations of the drive screw 30 and the driven screw 40, as indicated by the dashed arrow in Fig. As shown in Figure 1, the refrigerant is drawn from outside the compressor 1 through line H7 and the intake connection 69 into the intake chamber 65. As previously described, the refrigerant is cooled in the external heat exchanger 102 when the air conditioner 200 is in cooling mode. Accordingly, during cooling operation, the refrigerant is partially liquefied in the external heat exchanger 102 and stored as liquid refrigerant in the external heat exchanger 102. In the air conditioner 200, the external heat exchanger 102 is connected to the compressor 1 via pipe H4, pipe H5, the manifold 104, pipe H6, the evaporator 103, and pipe H7, while in heating mode, the external heat exchanger 102 is connected to the compressor 1 via pipe H4, pipe H10, and pipe H7.

[0094] Therefore, when the air conditioning system 200 is switched from cooling to heating mode, the refrigerant drawn into the intake chamber 65 through pipe H7 and intake port 69 can consist not only of the gaseous refrigerant, which is a vapor-phase refrigerant, but also of the liquid refrigerant stored in the external heat exchanger 102. The refrigerant drawn into the intake chamber 65 through pipe H7 and intake port 69 contains lubricating oil 18. For example, cooling mode can be switched to heating mode during the transition from summer to winter, and cooling mode can be temporarily switched to heating mode in summer if the temperature in the vehicle is incorrectly set.

[0095] In compressor 1, the refrigerant is drawn through pipe H7 and suction port 69 into the suction chamber 65, and the gas / liquid separation chamber 16 of the storage tank 15 receives the refrigerant from the suction chamber 65 via the suction flow path 151. The gas / liquid separation chamber 16 separates the refrigerant into gaseous and liquid refrigerant. In compressor 1, the refrigerant that has flowed through pipe H7 and suction port 69 is not drawn directly into the gas / liquid separation chamber 16, but rather via the suction chamber 65 into the gas / liquid separation chamber 16.

[0096] This means that in compressor 1, the refrigerant is drawn from outside the compressor 1 into the intake chamber 65 and initially separated into gaseous and liquid refrigerant within the intake chamber 65. Subsequently, the refrigerant is drawn from the intake chamber 65 through the intake flow path 151 into the gas / liquid separation chamber 16, where it is then separated into gaseous and liquid refrigerant.In compressor 1, the refrigerant is first separated in the intake chamber 65 into gaseous-liquid refrigerant and liquid refrigerant, so that the refrigerant drawn into the separation chamber 16 for gas and liquid is less likely to be liquid refrigerant compared to a configuration in which the refrigerant is drawn directly from outside the compressor 1 through the pipe H7 and the intake connection 69 into the separation chamber 16 for gas and liquid, and the refrigerant is only separated into gaseous refrigerant and liquid refrigerant in the separation chamber 16 for gas and liquid.

[0097] In addition to the lubricating oil 18 already present in the intake chamber 65, a portion of the lubricating oil 18 contained in the refrigerant drawn into the intake chamber 65 and a portion of the liquid refrigerant separated from the refrigerant in the intake chamber 65 are stored at the bottom of the intake chamber 65 due to gravity.

[0098] In compressor 1, the accumulator 15 is rotated by the rotor 11 around the drive axis O1 in the suction chamber 65. This causes the refrigerant drawn into the gas-liquid separation chamber 16 to be appropriately separated into gaseous and liquid refrigerants under the influence of the centrifugal force of the rotating accumulator 15. Due to centrifugal force, the liquid refrigerant, separated from the gaseous refrigerant, tends to remain on the radially outer side of the accumulator 15 in the gas-liquid separation chamber 16, i.e., on the radially outer side of the drive screw 30 and the driven 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 compressor 1, the cover body 35 of the drive screw 30 has the intake passage 35a and the supply passage 35b. This configuration allows the gaseous refrigerant in the gas / liquid separation chamber 16 to be drawn from the intake chamber 30a through the intake passage 35a into the compression chamber 12. The compression chamber 12 compresses the gaseous refrigerant and simultaneously reduces its volume through the rotation of the drive screw 30 and the driven screw 40. The gaseous refrigerant, compressed to an outlet pressure, is then expelled from the outlet opening 38 into the outlet chamber 13 and further expelled outside the compressor 1, i.e., to the condenser 101, via the pipe H1 connected to the outlet connection opening 68.

[0100] In the cover body 35, the intake passage 35a is located radially to the drive screw 30 within the supply passage 35b. This configuration of the compressor 1 prevents the liquid refrigerant in the gas-liquid separation chamber 16 from being drawn through the intake space 30a into the compression chamber 12, even if a large quantity of liquid refrigerant is present in the gas-liquid separation chamber 16. Since the intake passage 35a is connected to the gas-liquid separation chamber 16, the liquid refrigerant in the intake chamber 65 is not drawn into the intake passage 35a and thus into the compression chamber 12 without passing through the gas-liquid separation chamber 16. Accordingly, it is less likely that the compressor 1 will compress the liquid refrigerant in the compression chamber 12.

[0101] The gaseous refrigerant drawn into the compression chamber 12 through the intake port 35a contains a portion of the lubricating oil 18. The supply port 35b is located radially outside the intake port 35a of the drive screw 30. The supply port 35b opens into the gas-liquid separation chamber 16 at a position near the area where the lubricating oil 18 is present 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 via the supply port 35b. Accordingly, the compression chamber 12 in the compressor 1 is lubricated by the lubricating oil 18. Therefore, the tendency to wear of the drive screw end plate 31, the drive screw body 33, the end plate 41 of the driven screw and the body 43 of the driven screw of the compressor is lower.

[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, the liquid refrigerant evaporates as it flows through the supply passage 35b due to the heat generated by the drive screw 30 and the driven screw 40 during the operation of the compressor 1. Accordingly, 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, compressor 1 exhibits excellent reliability.

[0104] In particular, in the compressor 1, the first support section 64 has the return passage 8, and the return passage 8 is connected to the gas-liquid separation chamber 16 by holding the reservoir 15 in place. The return passage 8 is connected to the bottom of the intake chamber 65 via the first guide passage 62a and the second guide passage 62b of the attachment 62. This configuration of the compressor 1 allows the lubricating oil 18 stored at the bottom of the intake chamber 65 to flow into the gas-liquid separation chamber 16 through the first guide passage 62a, the second guide passage 62b, and the return passage 8. The lubricating oil 18 is supplied to the compression chamber 12 via the supply passage 35b in a suitable manner. Accordingly, the compression chamber 12 in the compressor 1 is lubricated in a suitable manner.Although some of the liquid refrigerant separated in the intake chamber 65 and stored at the bottom of the intake chamber 65 can flow into the gas and liquid separation chamber 16 together with the lubricating oil 18 flowing through the first guide passage 62a, the second guide channel 62b and the return passage 8, it is, as previously described, less likely in the compressor 1 that the liquid refrigerant in the gas and liquid separation chamber 16 will be drawn into the compression chamber 12 through the intake passage 35a and the supply passage 35b.

[0105] In compressor 1, the accumulator 15 is attached to the cover body 35 of the drive screw 30 and is located inside the rotor 11, and the accumulator 15 is attached to the inner circumferential surface of the rotor 11. Accordingly, the accumulator 15 in compressor 1 is not located completely outside the rotor 11. This configuration of compressor 1 reduces the need for an extension of the housing 6 in the direction of the drive axis O1. Furthermore, compressor 1 is able to transmit the power of the rotor 11 to the drive screw 30 via the accumulator 15, so that it is not necessary to connect the rotor 11 and the drive screw 30 directly for power transmission. Consequently, this configuration allows for greater flexibility in the design of the drive screw 30 of compressor 1.Therefore, this configuration of the compressor 1 allows for an increase in the diameters of the drive screw 30 and the driven screw 40 in order to adequately ensure the volume of the compression chamber 12, while reducing the need to increase the diameter of the casing 6 as much as possible. (Second embodiment)

[0106] Out of Fig. Figure 4 shows the compressor 2 according to the second embodiment, which has a storage tank 25 instead of the storage tank 15. In the compressor 2, the cover body 35 of the drive screw 30 has a feed passage 35c instead of the feed passage 35b. The feed passage 35c is located radially outside the intake passage 35a of the cover body 35. The feed passage 35c is formed by the cover body 35 in the forward / reverse direction and parallel to the drive axis O1.

[0107] The reservoir 25 is a tubular element with a base and has an outer wall 25a and a rear wall 25b. The outer wall 25a has a cylindrical shape centered around the drive axis O1. The outer diameter of the outer wall 25a is larger than that of the outer wall 15a of the reservoir 15 of the compressor 1 according to the first embodiment and has 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 reservoir 25 and has a substantially circular plate shape and is perpendicular to the drive axis O1. The outer circumferential edge of the rear wall 25b is connected to the rear end of the outer wall 25a.

[0108] The rear wall 25b has a through-hole 250 and an intake flow path 251 at the center of the rear wall 25b. The through-hole 250 and the intake flow path 251 have a similar structure to the through-hole 150 and the intake flow path 151 of the storage unit 15.

[0109] Similar to the compressor according to the first embodiment, in the compressor 2 the storage tank 25 is attached to the cover body 35 by the screws 50b.

[0110] Accordingly, a separation chamber 26 for gas and liquid is defined in the storage tank 25 by the outer wall 25a, the rear wall 25b of the storage tank 25, and the cover body 35. The separation chamber 26 for gas and liquid is connected to the intake passage 35a and the supply passage 35c.

[0111] The storage tank 25 is housed in the intake chamber 65 and rotatably mounted by the first support section 64. The separation chamber 26 for gas and liquid is connected to the intake chamber 65 via the intake flow path 251 and is also connected to the return flow passage 8.

[0112] In compressor 2, the electric motor 10 is located in front of the storage tank 25 within the intake chamber 65. The drive screw circumferential wall 32 of the drive screw 30 is inserted into the rotor 11 and attached to the inner circumferential surface of the rotor 11. It should be noted that other components of compressor 2 according to the second embodiment are identical to those of compressor 1 according to the first embodiment, and the components of the second embodiment that correspond to those of the first embodiment are designated with the same reference numerals and are not explained further here.

[0113] Similar to compressor 1 according to the first embodiment, compressor 2 is also used for the air conditioning system 200 (see Fig. 2 and Fig. 3) In compressor 2, the drive screw 30 and the accumulator 25 are rotated in the intake chamber 65 by the rotation of the rotor 11 about the drive axis O1. The refrigerant is supplied from outside compressor 1 through the pipe H7 and the intake connection 69, as indicated by the dashed arrow in Fig.As indicated in figure 4, the refrigerant is drawn into the intake chamber 65 and separated into gaseous and liquid refrigerant. The refrigerant in the intake chamber 65 is drawn through the intake flow path 251 into the gas-liquid separation chamber 26, and the liquid refrigerant is separated from the gas-liquid refrigerant in the gas-liquid separation chamber 26. The gaseous refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26 are drawn through the suction channel 35a and the supply channel 35c into the compression chamber 12. Compressor 2 can also exhibit the same effects as compressor 1 according to the first embodiment.

[0114] In compressor 2, the drive screw circumferential wall 32 is arranged inside the rotor 11 and attached to the inner circumferential surface of the rotor 11, and the accumulator 25 is attached to the cover body 35 of the drive screw 30. This configuration of compressor 2 eliminates the need to arrange the accumulator 25 inside the rotor 11, thus increasing flexibility in the design of the accumulator 25. In compressor 2, the diameter of the accumulator 25 is larger than that of the accumulator 15 of compressor 1 according to the first embodiment, thereby ensuring a suitable volume for the gas-liquid separation chamber 26. This facilitates the centrifugal separation of the liquid refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26.

[0115] Furthermore, the compressor 2 is able to transfer the power of the rotor 11 to the storage unit 25 via the drive screw 30, thus eliminating the need to directly connect the rotor 11 and the storage unit 25 for power transmission. In this respect, the configuration of the compressor 2 increases the design flexibility of the storage unit 25.

[0116] Although the present invention has been described with reference to the first and second embodiments, the present invention is not limited to these embodiments and can be modified in the field of the present invention.

[0117] For example, in the compressor 1 according to the first embodiment, both the cover body 35 and the end plate 41 of the driven screw can have the intake passage 35a, and both the cover body 35 and the end plate 41 of the driven screw can have the feed passage 35b. The same applies to the compressor 2 according to the second embodiment.

[0118] In the compressor 1 according to the first embodiment, the driven 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 driven screw 40 can be arranged outside the drive screw 30 and assembled with it. In this configuration, the end plate 41 of the driven screw can have the intake passage 35a and the feed passage 35b and be attached to the storage unit 15. The same applies to the compressor 2 according to the second embodiment.

[0119] In the compressor 1 according to the first embodiment, the drive screw 30 can be connected to the rotor 11 via a drive shaft for power transmission, such that the drive screw 30 and the 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.

[0120] In the compressor 1 according to the first embodiment, the drive mechanism 20 has the anti-rotation pins 21 and the rings 22. However, the present invention is not limited thereto, and the drive 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, by a pin-and-pin mechanism in which the outer circumferential surfaces of two pins slide against each other, by a mechanism using an Oldham shaft coupling, or the like. The same applies to the compressor 2 according to the second embodiment.

[0121] This description also applies to the following invention. (Supplementary Note 1)

[0122] A rotating screw compressor, comprising: a housing; a drive mechanism; a drive screw; a driven screw; and a driven mechanism, wherein the housing has an intake chamber in which the drive screw and the driven screw are housed and into which a refrigerant containing lubricating oil is drawn from outside the housing, the drive worm is configured to be rotated around a drive axis by the drive mechanism, The driven screw is arranged and configured eccentrically to the drive screw, to be rotated around an output axis by the drive screw and the drive mechanism, and the drive screw and the driven screw form a compression chamber for compressing the refrigerant, wherein a storage unit is included in the intake chamber, wherein the storage unit is connected to the intake chamber, the storage unit receives the refrigerant drawn in from the intake chamber and makes it possible to separate the refrigerant into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil, the storage unit is attached to the drive screw or the driven screw and is rotatable in the intake chamber, and at least one of the drive screw and the driven screw has an intake passage that is connected to the storage tank, and through which the gaseous refrigerant in the storage tank is drawn into the compression chamber. (Supplementary Note 2)

[0123] A rotating screw compressor according to supplementary note 1, wherein the housing has a support section extending into the intake chamber and supporting the storage unit in such a way that the storage unit is rotatable, and The support section has a return flow passage through which the lubricating oil in the intake chamber flows into the storage tank. (Supplementary Note 3)

[0124] A rotating screw compressor according to supplementary note 1 or 2, wherein at least one of the drive screw and the driven screw has a supply passage through which the lubricating oil in the reservoir of the compression chamber is supplied, and The feed passage is arranged in the radial direction of the drive screw and in the radial direction of the driven screw outside the suction passage and is connected to the storage tank. (Supplementary Note 4)

[0125] A rotating screw compressor according to one of Supplementary Notes 1 to 3, wherein the drive mechanism has: a stator located in the intake chamber and attached to the housing; and a cylindrical rotor rotatably arranged within the stator, and The storage unit is attached to the drive screw and arranged within the rotor. (Supplementary Note 5)

[0126] A rotating screw compressor according to one of Supplementary Notes 1 to 3, wherein the drive mechanism has: a stator which is housed in the intake chamber and attached to the casing; and a rotor having a cylindrical shape which is rotatably arranged in the stator, wherein The drive screw is arranged inside the rotor, and the storage unit is attached to the drive screw. INDUSTRIAL APPLICABILITY

[0127] The present invention is applicable to an air conditioning system and the like for a vehicle. REFERENCE MARK LIST 1, 2 compressors (rotating screw compressor) 6 cases 8 Backflow passage 10 Electric motor (drive mechanism) 11 Rotor 12 compression chambers 15, 25 storage 17 Stator 18 Lubricating oil 20 powered mechanism 30 drive worm 35a Intake passage 35b, 35c Inlet 40 driven auger 64 first support section (support section) 65 Intake chamber O1 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 - 076 287

[0005]

Claims

[1] A rotating screw compressor, which has: a housing; a drive mechanism; a drive screw; a driven screw; and a driven mechanism, wherein the housing has an intake chamber in which the drive screw and the driven screw are housed and into which a refrigerant containing lubricating oil is drawn from outside the housing, the drive worm is configured to be rotated around a drive axis by the drive mechanism, the driven screw is arranged eccentrically to the drive screw and configured to be rotated about an output axis by the drive screw and the drive mechanism, and the drive screw and the driven screw form a compression chamber for compressing the refrigerant, wherein a storage unit is included in the intake chamber, wherein the storage unit is connected to the intake chamber, the storage unit receives the refrigerant drawn in from the intake chamber and makes it possible to separate the refrigerant into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil, the storage unit is attached to the drive screw or the driven screw and is rotatable in the intake chamber, and at least one of the drive screw and the driven screw has an intake passage that is connected to the storage tank, and through which the gaseous refrigerant in the storage tank is drawn into the compression chamber. [2] A rotating screw compressor according to claim 1, wherein the housing has a support section extending into the intake chamber and supporting the storage unit in such a way that the storage unit is rotatable, and the support section has a return passage through which the lubricating oil in the intake chamber flows into the storage unit. [3] A rotating screw compressor according to claim 1 or 2, wherein at least one of the drive screw and the driven screw has a supply passage through which the lubricating oil is supplied to the reservoir of the compression chamber, and the supply passage is arranged outside the intake passage in the radial direction of the drive screw and in the radial direction of the driven screw and is connected to the reservoir. [4] A rotating screw compressor according to claim 1 or 2, wherein the drive mechanism has: a stator which is housed in the intake chamber and attached to the housing; and a rotor having a cylindrical shape which is rotatably arranged inside the stator, and the accumulator is attached to the drive screw and arranged in the rotor. [5] A rotating screw compressor according to claim 1 or 2, wherein the drive mechanism has: a stator which is housed in the intake chamber and attached to the housing; and a rotor having a cylindrical shape which is rotatably arranged in the stator, wherein the drive screw is arranged inside the rotor, and the storage unit is attached to the drive screw.

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