JP2015028313A - Axial vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an axial vane type compressor of a two-stage boosting type, which can properly compress fluid.SOLUTION: As a plurality of vanes 14 slidably fitted in a slit groove formed on a rotor 13, vanes in which dimensions in a diametrical direction of a front side projecting portion 14b projecting out from the rotor 13 toward a front housing 11b side are formed to be longer than dimensions in a diametrical direction of a rear side projecting portion 14c projecting from the rotor 13 toward a rear housing 11c are adopted. Therefore, the maximum capacity of a front side compression chamber formed on one end side of the rotor 13 is made to be larger than the maximum capacity of a rear side compression chamber formed on the other end side of the rotor 13, and both compression chambers are connected in series to configure a compressor of a two-stage boosting type.

Description

  The present invention relates to an axial vane compressor in which a plurality of flat vanes are reciprocally displaced in the axial direction of a rotating shaft.

  Conventionally, Patent Document 1 discloses a compressor applicable to a vapor compression refrigeration cycle, in which a plurality of plate-shaped vanes extending in the radial direction and the axial direction of a rotary shaft are rotationally displaced around the axis of the rotary shaft. However, an axial vane type compressor that compresses and discharges fluid by reciprocating displacement in the axial direction of the rotating shaft is disclosed.

  More specifically, the axial vane compressor of Patent Document 1 includes a cylinder that forms a cylindrical space inside, a cylindrical rotor that is disposed inside the cylinder and rotates with a rotation shaft (shaft), and the like. Each vane is slidably disposed in a slit groove formed in the rotor.

  Furthermore, a cylindrical ring that restricts the displacement of the vane in the radial direction is disposed between the outer peripheral side of the vane and the inner peripheral side of the cylinder, and the axial end of the vane is disposed at each axial end of the vane. A front side plate and a rear side plate are provided on which cam surfaces are formed that come into contact with the portion to displace the vanes in the axial direction.

  Thereby, in the axial vane type compressor of patent document 1, the space surrounded by the axial end surface of the rotor, the flat surface of the adjacent vane, the inner peripheral surface of the ring, the cam surface of each side plate, etc. Two compression chambers are formed on both ends in the axial direction, and the fluid is compressed and discharged by periodically changing the volumes of both compression chambers.

JP-A-56-18092

  Incidentally, in a vapor compression refrigeration cycle, a gas injection cycle (economizer refrigeration cycle) is known as a cycle configuration for improving the coefficient of performance (COP) of the cycle. In this type of gas injection cycle, the intermediate pressure refrigerant generated in the cycle is joined to the intermediate pressure refrigerant in the pressurization process by the compressor, thereby improving the compression efficiency of the compressor and reducing the COP as the entire cycle. It is improving.

  For this reason, as a compressor applied to a gas injection cycle, a two-stage boosting type that boosts the refrigerant in multiple stages in two compression chambers may be employed. The reason is that in a two-stage booster compressor, one compression chamber functions as a low-stage compression chamber that pressurizes low-pressure refrigerant until it becomes intermediate-pressure refrigerant, and the other compression chamber functions as high-pressure refrigerant. This is because the intermediate-pressure refrigerant generated in the cycle can be easily merged with the refrigerant in the pressurization process in the compressor by functioning as the high-stage side compression chamber that is pressurized until the pressure increases.

  However, in the two-stage booster type compressor, the density of the refrigerant sucked into the low-stage side compression chamber is different from the density of the refrigerant sucked into the high-stage side compression chamber. It is desirable to set different values for the discharge capacity (maximum volume) of the lower stage compression chamber and the discharge capacity (maximum volume) of the higher stage compression chamber.

  Furthermore, in the two-stage booster compressor applied to the gas injection cycle, not only the density of the refrigerant sucked into the low-stage compression chamber is different from the density of the refrigerant sucked into the high-stage compression chamber, The mass flow rate of the refrigerant sucked into the compression chambers is also different. Therefore, unless the discharge capacity of the low-stage compression chamber and the discharge capacity of the high-stage compression chamber are set appropriately, the above-described COP improvement effect cannot be obtained sufficiently.

  For this reason, like the axial vane type compressor of patent document 1, the maximum protrusion length of the vane which protrudes from a rotor to both compression chambers corresponds, and the discharge capacity (maximum volume) of both compression chambers corresponds. In such a configuration, it is difficult to appropriately compress the fluid as a two-stage booster type compressor even if two compression chambers are simply connected in series. Furthermore, when applied to a gas injection cycle, a sufficient COP improvement effect cannot be obtained.

  An object of this invention is to provide the two-stage pressure | voltage rise type axial vane type compressor which can compress a fluid appropriately in view of the said point.

  Another object of the present invention is to provide a two-stage booster type axial vane compressor suitable for a gas injection cycle.

The present invention has been devised in order to achieve the above object. In the first aspect of the present invention, a rotating shaft (12) that rotates when a rotational driving force is transmitted, and a rotating shaft on the outer peripheral surface. A plurality of slit grooves (13a) extending in the axial direction of (12) are formed, a cylindrical rotor (13) coaxially connected to the rotating shaft (12), and the diameter of the rotating shaft (12) A plurality of vanes (14) formed in a flat plate shape extending in parallel with the direction and the axial direction, and slidably fitted in the slit grooves (13a), and abutting with an end of one end of the vane (14) in the axial direction. A front side plate (16) having a front cam surface (16a) for displacing the vane (14) in the axial direction as the vane (14) is rotationally displaced about the rotation shaft (12). , End on the other axial end side of the vane (14) The rear side plate (17) is formed with a rear cam surface (17a) that displaces the vane (14) in the axial direction as the vane (14) is rotationally displaced about the rotation shaft (12). ) And cylinders (18, 19, 20) disposed on the outer peripheral side of the rotor (13), the front side plate (16), and the rear side plate (17).
The fluid is surrounded by the space surrounded by the end surface on one end side in the axial direction of the rotor (13), the flat surface of the adjacent vane (14), the front cam surface (16a), and the inner peripheral surface of the cylinder (18-20). A front-side compression chamber (23b) for compression is formed, the end surface on the other end side in the axial direction of the rotor (13), the flat surface of the adjacent vane (14), the rear cam surface (17a), and the cylinders (18 to 20) ), A rear side compression chamber (23c) for compressing fluid is formed by the space surrounded by the inner peripheral surface of
The axial vane type compressor is characterized in that the maximum volume of the front side compression chamber (23b) and the maximum volume of the rear side compression chamber (23c) are different values.

  According to this, since the maximum volume (discharge capacity) of the front side compression chamber (23b) and the maximum volume (discharge capacity) of the rear side compression chamber (23c) have different values, the front side compression chamber (23b) ) And the rear side compression chamber (23c) in series can provide a two-stage boosting type axial vane compressor capable of appropriately compressing fluid.

  Further, in the axial vane type compressor having the above characteristics, the side having the largest maximum volume among the front side compression chamber (23b) and the rear side compression chamber (23c) is the large capacity side compression chamber (23b), and the maximum volume is small. When the side is the small-capacity compression chamber (23c), the fluid obtained by joining the intermediate-pressure fluid sucked from the outside and the intermediate-pressure fluid discharged from the large-capacity compression chamber (23b) It is characterized by being sucked into the compression chamber (23c).

  According to this, the large-capacity compression chamber (23b) and the small-capacity compression chamber (23c) are connected in series, and are further discharged from the externally sucked intermediate pressure fluid and the large-capacity compression chamber (23b). Since the fluid combined with the intermediate pressure fluid is sucked into the small-capacity compression chamber (23c), a two-stage booster type axial vane compressor suitable for a gas injection cycle is provided. Can do.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole lineblock diagram of the refrigerating cycle of a 1st embodiment. It is an axial sectional view of the compressor of a 1st embodiment. It is III-III sectional drawing of FIG. It is IV-IV sectional drawing of FIG. It is an external appearance perspective view of the front side plate of the compressor of a 1st embodiment. It is explanatory drawing for demonstrating the locus line which the contact part of the cam surface and vane of the compressor of 1st Embodiment draws. It is a perspective view which shows the assembly | attachment states, such as a rotor, a vane, and a side plate, of the compressor of 1st Embodiment. It is an axial sectional view of the compressor of the second embodiment. It is an axial direction sectional view of the compressor of a 3rd embodiment.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. A two-stage booster type axial vane compressor 1 (hereinafter simply referred to as a compressor 1) of the present embodiment is applied to a refrigeration cycle 100 shown in the overall configuration diagram of FIG. The refrigeration cycle 100 functions to cool indoor air blown into a room in an air conditioner that performs indoor air conditioning.

  Specifically, the refrigeration cycle 100 of the present embodiment exchanges heat between the compressor 1 that compresses and discharges the refrigerant, and the high-pressure refrigerant discharged from the compressor 1 and outdoor air (outside air). The radiator 2 that radiates heat, the three-way joint 3 that functions as a branching part that branches the flow of the high-pressure refrigerant that has flowed out of the radiator 2, and the one high-pressure refrigerant that is branched by the three-way joint 3 is reduced to an intermediate pressure refrigerant. An internal heat exchanger 5 for exchanging heat between the high-stage expansion valve 4 to be made, the other high-pressure refrigerant branched by the three-way joint 3 and the intermediate-pressure refrigerant decompressed by the high-stage expansion valve 4, and internal heat The low-stage expansion valve 6 that decompresses the high-pressure refrigerant that has flowed out of the exchanger 5 until it becomes a low-pressure refrigerant, and the low-pressure refrigerant that has flowed out of the low-stage expansion valve 6 and the indoor blowing air are heat-exchanged to evaporate the low-pressure refrigerant. Vapor compression type refrigeration unit comprising an evaporator 7 It is a cycle.

  Furthermore, in the refrigeration cycle 100 of the present embodiment, the intermediate pressure refrigerant decompressed by the high stage side expansion valve 4 is supplied to the intermediate pressure refrigerant inlet of the compressor 1 via the intermediate pressure refrigerant passage of the internal heat exchanger 5. 11f. That is, in the refrigeration cycle 100 of the present embodiment, the intermediate-pressure refrigerant generated in the cycle (specifically, decompressed by the high-stage expansion valve 4) is compressed by the compressor 1 in the intermediate-pressure refrigerant. It is configured as a gas injection cycle (economizer-type refrigeration cycle) that joins the two.

  The refrigeration cycle 100 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. Of course, an HFO refrigerant (for example, R1234yf) or the like may be adopted as the refrigerant. Furthermore, the refrigerating machine oil for lubricating the compressor 1 is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  Next, the detailed structure of the compressor 1 of this embodiment is demonstrated. As shown in FIGS. 2 to 4, the compressor 1 includes a shaft 12, a rotor 13, a front side plate 16, a rear side plate 17, cylinders 18, 19, 20, and the like inside a housing 11 that forms an outer shell thereof. Contained and configured.

  The housing 11 is configured by combining a plurality of constituent members, and forms a substantially columnar sealed space inside. More specifically, the housing 11 includes a middle housing 11a formed in a cylindrical shape, a disk-shaped front housing 11b and a rear housing 11c that close the openings on both axial ends of the middle housing 11a. .

  Two communicating holes penetrating the inside and the outside are formed in the cylindrical side surface of the middle housing 11a, and one communicating hole constitutes a low-pressure refrigerant inlet 11d for sucking low-pressure refrigerant from the outside of the housing 11. Yes. The other communication hole constitutes a high-pressure refrigerant discharge port 11 e for discharging high-pressure refrigerant from the inside of the housing 11.

  A front bush 21b formed of a cylindrical member protruding toward the rear housing 11c is fixed to the center of the front housing 11b. Further, a front bearing 22b that rotatably supports one end of the shaft 12 is fixed to the inner peripheral side of the front bush 21b.

  Similarly, a rear bush 21c formed of a cylindrical member protruding toward the front housing 11b is fixed to the center of the rear housing 11c. Further, a rear bearing 22c that rotatably supports the other end of the shaft 12 is fixed to the inner peripheral side of the rear bush 21c.

  The center axis of the front bush 21 b and the center axis of the rear bush 21 c are arranged coaxially with the center axis of the shaft 12. Furthermore, the outer diameter dimension of the rear bush 21c is formed larger than the outer diameter dimension of the front bush 21b. As the front bearing 22b and the rear bearing 22c, either a rolling bearing or a sliding bearing may be adopted.

  Further, the front housing 11 b is formed with a communication hole penetrating the inside and outside of the front housing 11 b, and this communication hole constitutes an intermediate pressure refrigerant suction port 11 f for sucking the intermediate pressure refrigerant from the outside of the housing 11.

  The shaft 12 is a rotating shaft that rotates when a rotational driving force is transmitted from the driving source M. An end portion on the front housing 11b side which is one end side of the shaft 12 protrudes to the outside of the housing 11 through a through hole provided in the center portion of the front housing 11b. Note that a seal member (not shown) is disposed in the through hole of the front housing 11b, so that the refrigerant does not leak from the gap between the through hole and the shaft 12.

  Further, a drive source M is connected to a portion of the shaft 12 that protrudes to the outside from the front housing 11b. The drive source M may be an electric motor or an internal combustion engine (engine). Further, the drive source M may be connected to the shaft 12 so as to be able to directly transmit the rotational driving force, or indirectly connected to the shaft 12 via a pulley, a belt, or the like. Also good.

  Further, a rotor 13 formed in a columnar shape is connected to the shaft 12 coaxially with the shaft 12. More specifically, the rotor 13 is disposed between the front bush 21b and the rear bush 21c. In this embodiment, the shaft 12 and the rotor 13 are integrally connected by a single member. However, the shaft 12 and the rotor 13 are formed by different members, and the rotor 13 is disposed on the outer periphery of the shaft 12. You may connect by means, such as press injection.

  A plurality of slit grooves 13 a extending in the axial direction of the shaft 12 are formed on the outer peripheral surface of the rotor 13. More specifically, as shown in FIGS. 3 and 4, four slit grooves 13a are formed on the outer peripheral surface of the rotor 13 of the present embodiment, and each slit groove 13a is viewed from the axial direction. Are arranged at equiangular intervals (in this embodiment, 90 ° intervals).

  A flat plate-like vane 14 extending in parallel to the radial direction and the axial direction of the shaft 12 is fitted in each slit groove 13 a so as to be slidable in the axial direction of the shaft 12. Although the vane 14 is a plate-like member formed in a flat plate shape, each corner is subjected to C chamfering or R chamfering so that the slit groove 13a can be smoothly slid. Yes.

  A ring 15 formed in a cylindrical shape is fixed to the outer peripheral side of the rotor 13 by means such as press-fitting, and the displacement of the vane 14 toward the outer peripheral side in the radial direction is restricted by the ring 15.

  Furthermore, in this embodiment, the flat surface of the vane 14 is not simply formed in a rectangular shape, but as shown in FIG. 2, a portion that protrudes from the rotor 13 toward the front housing 11 b (front side protrusion). Portion) 14b and a portion (rear side protruding portion) 14c protruding from the rotor 13 toward the rear housing 11c are employed.

  More specifically, in the present embodiment, as shown in FIGS. 3 and 4, the vane 14 is notched on the inner peripheral side of the rear side protruding portion 14 c when viewed from the axial direction of the shaft 12. Therefore, the rear-side protruding portion 14c has a shorter radial dimension than the front-side protruding portion 14b.

  As described above, in the present embodiment, the outer diameter of the rear bush 21 is formed larger than the outer diameter of the front bush 21b. Therefore, in the present embodiment, when viewed from the axial direction of the shaft 12, a range where the vane 14 and the rear bush 21 overlap is cut out from the rear side protruding portion 14 c when viewed from the axial direction of the shaft 12. As a result, the displacement of the vane 14 in the axial direction is prevented from being restricted by the rear bush 21c.

  In addition, as shown in FIG. 2, a front side plate 16 is disposed on one end side (front housing 11b side) of the vane 14 and on the other end side (rear housing 11c side) of the vane 14 in the axial direction. A rear side plate 17 is disposed.

  The front side plate 16 is formed in an annular shape when viewed from the axial direction, and is fixed to the outer peripheral side of the front bush 21b by means such as press fitting. Further, the front side plate 16 abuts against the axial end portion of the vane 14 on the front housing 11b side, and the vane 14 rotates in the axial direction as the vane 14 rotates around the axis of the shaft 12 together with the rotor 13. A front cam surface 16a to be displaced is formed.

  On the other hand, the rear side plate 17 is formed in an annular shape when viewed from the axial direction, and is fixed to the outer peripheral side of the rear bush 21c by means such as press fitting. Further, the rear side plate 17 contacts the axial end of the vane 14 on the rear housing 11c side, and the vane 14 is displaced in the axial direction as the vane 14 rotates around the shaft 12 along with the rotor 13. A rear side cam surface 17a is formed.

  The outer diameters of the front side plate 16 and the rear side plate 17 are formed substantially equal to the outer diameter of the rotor 13. On the other hand, the inner diameter of the front side plate 16 is smaller than the inner diameter of the rear side portion rate. For this reason, when viewed from the axial direction, the radial width dimension of the front cam surface 16a formed in an annular shape (the dimension obtained by subtracting the inner peripheral radius from the outer peripheral radius) is the same as that of the rear cam surface 17a. It is longer than the width dimension in the radial direction.

  Here, specific shapes of the front-side cam surface 16a and the rear-side cam surface 17a will be described with reference to FIG. Although the front cam surface 16a and the rear cam surface 17a have different widths in the radial direction but have the same basic shape, FIG. 5 shows the front cam surface 16a of the front side plate 16. The corresponding part of the rear side cam surface 17a of the rear side plate 17 is shown with parentheses.

  As shown in FIG. 5, the front side cam surface 16a includes a top side flat surface portion 16b extending vertically in the axial direction at a position closest to the rear housing 11c side of the front side cam surface 16a, and a front side cam surface 16a. Among them, a bottom side plane portion 16c that extends vertically in the axial direction at a position farthest from the rear housing 11c side, and a curved surface portion 16d that is curved so as to connect the top side plane portion 16b and the bottom side plane portion 16c are provided. Yes.

  The top side plane portion 16b and the bottom side plane portion 16c are arranged at positions that are symmetrical with respect to the axis center of the shaft 12 when viewed from the axial direction (that is, positions rotated by 180 ° around the axis). ing. Furthermore, as shown in FIG. 2, the top side plane part 16b is arrange | positioned on the same plane as the end surface by the side of the rear housing 11c of the front bush 21b.

  Similarly, the rear side cam surface 17a of the rear side plate 17 is provided with a top side plane portion 17b, a bottom side plane portion 17c, and a curved surface portion 17d. The top side plane portion 17b of the rear side cam surface 17a is The bush 21c is formed on the same plane as the end surface of the front housing 11b side.

  Further, when the front side plate 16 and the rear side plate 17 are viewed in the axial direction, the top side flat surface portion 16b of the front side cam surface 16a and the bottom side flat surface portion 17c of the rear side cam surface 17a are overlapped, and the front side cam 16 It arrange | positions so that the bottom part side plane part 16c of the surface 16a and the top part side plane part 17b of the rear side cam surface 17a may overlap.

  Thus, in the present embodiment, the axial distance between the portions of the front side cam surface 16a and the rear side cam surface 17a facing each other in the axial direction is the axial length of the vane 14 (axis It is equivalent to the length between the direction end portions). Therefore, when the rotor 13 rotates together with the shaft 12, the axial end of the vane 14 contacts the front cam surface 16a and the rear cam surface 17a and is displaced in the axial direction.

  At this time, the top side plane portions 16b and 17b and the bottom side plane portions 16c and 17c (hereinafter, these surfaces are collectively referred to as a plane portion) are formed by planes extending perpendicularly to the axial direction. Therefore, even if the vane 14 in contact with the flat portions 16b, 16c, 17b, and 17c rotates around the axis of the shaft 12 together with the rotor 13, it does not displace in the axial direction.

  On the other hand, since the curved surface portions 16d and 17d are formed with curved surfaces so as to connect the top side plane portions 16b and 17b and the bottom side plane portions 16c and 17c, the vane 14 that contacts the curved surface portions 16d and 17d. Is displaced in the axial direction while rotating around the axis of the shaft 12 together with the rotor 13.

  Therefore, as shown in FIG. 6, the vane 14 of the present embodiment has a rotation angle θ of 0 ° when the rotation angle θ of the rotor 13 when the vane 14 moves to the most end side (front housing 11 b side) is 0 °. When the angle reaches 180 °, the vane 14 moves to the other end side (rear housing 11c side), and when the rotation angle θ reaches 360 °, the vane 14 moves toward the one end side again. That is, when the rotor 13 makes one revolution, the vane 14 reciprocates once in the axial direction.

  In FIG. 6, the locus lines drawn by the contact portions when the contact portions between the cam surfaces 16 a and 17 a and the vanes 14 are viewed from the radial direction of the shaft 12 while rotating together with the shaft 12 are indicated by bold lines. Yes.

  Further, as shown in FIG. 5, the refrigerant inlets of the plurality of discharge refrigerant passages 16e that communicate the front side cam surface 16a side and the back side of the front side cam surface 16a with the top side flat surface portion 16b of the front side cam surface 16a. The part is open. In FIG. 5, three refrigerant inlet portions of the discharge refrigerant passages 16e and 17e are arranged in the radial direction. However, in other drawings, the discharge refrigerant passages 16e and 17e are shown for clarity of illustration. Only one of them is shown.

  The discharge refrigerant passage 16e allows communication between a later-described front-side compression chamber 23b formed by the front-side cam surface 16a and an intermediate pressure chamber 11g formed by the surface on the back side of the front-side cam surface 16a of the front side plate 16. It is a refrigerant passage. Furthermore, a reed valve (discharge valve) (not shown) that prohibits refrigerant from flowing backward from the intermediate pressure chamber 11g to the front compression chamber 23b is disposed at the outlet portion of the discharge refrigerant passage 16e on the intermediate pressure chamber 11g side. .

  The intermediate pressure chamber 11 g is disposed between the front side plate 16 and the front housing 11 b and is formed in an annular shape around the shaft 12. Furthermore, the intermediate pressure refrigerant suction port 11f formed in the front housing 11b described above is formed to guide the intermediate pressure refrigerant sucked from the outside of the housing 11 to the intermediate pressure chamber 11g. Further, as shown in FIGS. 2 and 4, the intermediate pressure chamber 11g communicates with an intermediate pressure refrigerant suction chamber 11m described later via an intermediate pressure communication passage 11h provided in the middle housing 11a.

  Similarly, refrigerant inlet portions of a plurality of discharge refrigerant passages 17e that open the rear side cam surface 17a and the rear side of the rear side cam surface 17a are opened in the top side plane portion 17b of the rear side cam surface 17a. .

  The discharge refrigerant passage 17e is a refrigerant passage that communicates a rear side compression chamber 23c, which will be described later, formed by the rear side cam surface 17a, and a discharge chamber 11i formed by a space between the rear side plate 17 and the rear housing 11c. is there. Furthermore, a reed valve (discharge valve) (not shown) that prohibits the refrigerant from flowing backward from the discharge chamber 11i to the rear side compression chamber 23c is also arranged at the outlet of the discharge refrigerant passage 17e on the discharge chamber 11i side.

  The discharge chamber 11 i is disposed between the rear side plate 17 and the rear housing 11 c and is formed in an annular shape around the shaft 12. Further, as shown in FIG. 2, the discharge chamber 11i communicates with the above-described high-pressure refrigerant discharge port 11e via a high-pressure communication passage 11j provided in the middle housing 11a.

  Next, on the outer peripheral side of the front side plate 16, the rotor 13, the ring 15, and the rear side plate 17, a cylinder configured by combining a plurality of constituent members is disposed. The cylinder is arranged coaxially with the shaft 12 and forms a cylindrical space in which the rotor 13, the vane 14 and the like are accommodated.

  More specifically, the cylinder of the present embodiment includes a front side cylinder 19 press-fitted and fixed to the outer peripheral side of the front side plate 16 and the inner peripheral side of the middle housing 11a, the outer peripheral side of the rear side plate 17 and the inner side of the middle housing 11a. The rear side cylinder 20 is press-fitted and fixed to the peripheral side, and the middle cylinder 18 is press-fitted and fixed to the inner peripheral side of the middle housing 11a with both axial ends fixed to the front side cylinder 19 and the rear side cylinder 20. ing.

  The end surface on the rear housing 11c side of the front side cylinder 19 is formed on the same plane as the top side flat surface portion 16b of the front side cam surface 16a and the end surface on the rear housing 11c side of the front bush 21b.

  Thereby, in this embodiment, as shown in FIG. 7, the end surface of the rotor 13 at one end side in the axial direction (front housing 11b side), the flat surface of the adjacent vane 14, the front cam surface 16a, and the outer periphery of the front bush 21b A plurality of (four in the present embodiment) front side compression chambers 23b for compressing the refrigerant are formed by the space surrounded by the surface and the inner peripheral surface (not shown in FIG. 7) of the front side cylinder 19. Yes.

  Further, as shown in FIG. 2, the front side cylinder 19 includes a front side compression chamber 23b having a maximum volume on the bottom side flat surface part 16c side of the front side cam surface 16a and an inner peripheral side of the middle housing 11a. A suction passage 19a that communicates with the formed low-pressure refrigerant suction chamber 11k is formed. The suction passage 19 a extends in the radial direction, and the refrigerant inlet portion opens on the outer peripheral wall surface of the front side cylinder 19.

  The low-pressure refrigerant suction chamber 11k is a space into which the low-pressure refrigerant sucked from the low-pressure refrigerant suction port 11d of the middle housing 11a flows, and the inner circumference side of the middle housing 11a and the outer circumference side of the front side cylinder 19 and the middle cylinder 18 It is a space formed in a cylindrical shape.

  On the other hand, the end surface on the front housing 11b side of the rear side cylinder 20 is formed on the same plane as the top side flat surface portion 17b of the rear side cam surface 17a and the end surface on the front housing 11b side of the rear bush 21c.

  Thereby, in this embodiment, as shown in FIG. 7, the end surface on the other axial end side (rear housing 11c side) of the rotor 13, the flat surface of the adjacent vane 14, the rear cam surface 17a, and the rear bush 21c. A plurality of (four in this embodiment) rear side compression chambers 23c for compressing the refrigerant are formed by a space surrounded by the outer peripheral surface and the inner peripheral surface (not shown in FIG. 7) of the rear side cylinder 20. Yes.

  Here, as described above, in the present embodiment, the outer diameter of the rear bush 21 is formed larger than the outer diameter of the front bush 21b. Accordingly, the maximum volume (discharge capacity) of the rear side compression chamber 23c when the end surface on the other end side in the axial direction of the rotor 13 and the rear side cam surface 17a are farthest is the end surface on the one end side in the axial direction of the rotor 13 and the front side. It becomes smaller than the maximum volume (discharge capacity) of the front side compression chamber 23b when the cam surface 16a is farthest away.

  That is, the front side compression chamber 23b of the present embodiment constitutes the large capacity side compression chamber described in the claims, and the rear side compression chamber 23c is the small capacity side described in the claims. It constitutes a compression chamber.

  Further, in the present embodiment, the refrigerant compressed in the front side compression chamber 23b has an intermediate pressure at which the coefficient of performance (COP) of the cycle approaches the maximum value during normal operation of the refrigeration cycle 100. The volume ratio between the maximum volume of 23b and the maximum volume of the rear side compression chamber 23c is adjusted. Such adjustment of the volume ratio can be easily realized by adjusting the outer dimensions of the front bush 21b and the rear bush 21c.

  Further, as shown in FIG. 2, the rear side cylinder 20 communicates with the rear side compression chamber 23c having the maximum volume on the bottom side flat surface portion 17c side of the rear side cam surface 17a and the intermediate pressure refrigerant suction chamber 11m. A suction passage 20a is formed. The suction passage 20 a extends in the radial direction, and the refrigerant inlet portion opens on the outer peripheral wall surface of the rear side cylinder 20.

  The intermediate pressure refrigerant suction chamber 11m is a space through which the intermediate pressure refrigerant in the intermediate pressure chamber 11g flows into the intermediate pressure refrigerant through the intermediate pressure communication passage 11h, and is provided on the inner side of the middle housing 11a and on the rear side cylinder 20 A space formed in a cylindrical shape on the outer peripheral side of the middle cylinder 18.

  The middle cylinder 18 is a cylindrical member disposed on the outer peripheral side of the ring 15 and is press-fitted into the inner peripheral side of the middle housing 11a, thereby partitioning the low-pressure refrigerant suction chamber 11k and the intermediate-pressure refrigerant suction chamber 11m. doing. Further, the inner diameter of the middle cylinder 18 is formed larger than the outer diameter of the ring 15, and the axial length of the middle cylinder 18 is formed longer than the axial length of the ring 15.

  Next, the operation of the compressor 1 and the refrigeration cycle 100 of the present embodiment in the above configuration will be described. When the rotational driving force is transmitted from the driving source M and the shaft 12 and the rotor 13 rotate, the vane 14 reciprocates in the axial direction of the shaft 12 while being rotationally displaced together with the rotor 13. Thereby, the front side compression chamber 23b and the rear side compression chamber 23c are rotationally displaced around the axis of the shaft 12 while changing the volume.

  Then, the low-pressure refrigerant sucked into the low-pressure refrigerant suction chamber 11k in the housing 11 from the low-pressure refrigerant suction port 11d passes through a suction passage 19a formed in the front side cylinder 19 and has a maximum volume. It flows into 23b.

  In the front-side compression chamber 23b having the maximum volume, the front-side cam surface 16a and the end surface on the one end side in the axial direction of the rotor 13 are farthest apart. Therefore, when the shaft 12 further rotates and the front-side compression chamber 23b is rotationally displaced, the front-side cam surface 16a and the end surface on one end side of the rotor 13 approach each other, and the volume of the front-side compression chamber 23b is reduced. Thereby, the refrigerant in the front side compression chamber 23b is compressed until it becomes an intermediate pressure refrigerant.

  Further, when the shaft 12 rotates and the front side compression chamber 23b approaches the minimum volume, the front side compression chamber 23b and the intermediate pressure chamber 11g communicate with each other through the discharge refrigerant passage 16e formed in the front side plate 16. . Thereby, the intermediate pressure refrigerant compressed in the front side compression chamber 23b flows into the intermediate pressure chamber 11g.

  When the shaft 12 further rotates from the state in which the front side compression chamber 23b has the minimum volume, the front side cam surface 16a and the end surface on one end side of the rotor 13 are separated from each other, and the volume of the front side compression chamber 23b is increased. . When the front side compression chamber 23b approaches the maximum volume, the low-pressure refrigerant flows into the front side compression chamber 23b via the suction passage 19a.

  The intermediate pressure refrigerant flowing into the intermediate pressure chamber 11g from the front-side compression chamber 23b merges with the intermediate pressure refrigerant sucked into the intermediate pressure chamber 11g from the intermediate pressure refrigerant suction port 11f, and the intermediate pressure refrigerant passes through the intermediate pressure communication passage 11h. It flows into the suction chamber 11m. The refrigerant that has flowed into the intermediate-pressure refrigerant suction chamber 11m flows into the rear-side compression chamber 23c having the maximum volume via the suction passage 20a formed in the rear side cylinder 20.

  In the rear side compression chamber 23c having the maximum volume, the rear side cam surface 17a and the end surface on the other end side (the rear housing 11c side) of the rotor 13 are farthest apart. Accordingly, when the shaft 12 further rotates and the rear side compression chamber 23c is rotationally displaced, the rear side cam surface 17a and the end surface on the other end side of the rotor 13 approach each other, and the volume of the rear side compression chamber 23c is reduced. As a result, the refrigerant in the rear side compression chamber 23c is compressed until it becomes a high-pressure refrigerant.

  Further, when the shaft 12 rotates and the rear side compression chamber 23c approaches the minimum volume, the rear side compression chamber 23c and the discharge chamber 11i communicate with each other through the discharge refrigerant passage 17e formed in the rear side plate 17. Thereby, the high-pressure refrigerant compressed in the rear side compression chamber 23c flows into the discharge chamber 11i. The high-pressure refrigerant flowing into the discharge chamber 11i is discharged from the high-pressure refrigerant discharge port 11e through the high-pressure communication path 11j.

  When the shaft 12 further rotates from the state in which the rear side compression chamber 23c has the minimum volume, the rear side cam surface 17a and the end surface on the other end side of the rotor 13 are separated from each other, and the volume of the rear side compression chamber 23c is increased. To do. When the rear side compression chamber 23c approaches the maximum volume, the intermediate pressure refrigerant flows into the rear side compression chamber 23b through the suction passage 20a.

  Further, in the refrigeration cycle 100, the high-pressure refrigerant discharged from the high-pressure refrigerant discharge port 11e of the compressor 1 flows into the radiator 2, is cooled by heat exchange with the outside air, and is condensed. The flow of the refrigerant that has flowed out of the radiator 2 is branched at the branching section 3.

  One of the high-pressure refrigerants branched at the branching part 3 is decompressed until it becomes intermediate-pressure refrigerant at the high-stage expansion valve 4 and flows into the intermediate-pressure refrigerant passage of the internal heat exchanger 5. The other high-pressure refrigerant branched by the branch part 3 flows into the high-pressure refrigerant passage of the internal heat exchanger 5. In the internal heat exchanger 5, the intermediate pressure refrigerant whose temperature has been reduced by being reduced in pressure is heated by the high pressure refrigerant, and the high pressure refrigerant is further cooled by the intermediate pressure refrigerant.

  The high-pressure refrigerant that has flowed out of the high-pressure refrigerant passage of the internal heat exchanger 5 is decompressed by the low-stage expansion valve 6 until it becomes low-pressure refrigerant, and flows into the evaporator 7. The refrigerant flowing into the evaporator 7 absorbs heat from the indoor air and evaporates. Thereby, indoor ventilation air is cooled.

  The refrigerant flowing out of the evaporator 7 is sucked from the low-pressure refrigerant suction port 11d of the compressor 1 and compressed again. On the other hand, the intermediate pressure refrigerant flowing out from the intermediate pressure refrigerant passage of the internal heat exchanger 5 is sucked from the intermediate pressure refrigerant suction port 11 f of the compressor 1.

  As described above, the compressor 1 of the present embodiment functions as a two-stage booster type compressor because the front side compression chamber 23b and the rear side compression chamber 23c are connected in series. Furthermore, in the compressor 1 of the present embodiment, the maximum volume (discharge capacity) of the front side compression chamber 23b and the maximum volume (discharge capacity) of the rear side compression chamber 23c are different values. The refrigerant can be appropriately compressed as a compressor.

  More specifically, in the compressor 1 of the present embodiment, the shape of the front side protruding portion 14b of the vane 14 and the shape of the rear side protruding portion 14c are different from each other (specifically, the front side protruding portion 14b The radial dimension is different from the radial dimension of the rear-side protruding portion 14c).

  Thus, the axial vane type compressor in which the maximum protruding length of the vane 14 protruding from the rotor 13 to the front side compression chamber 23b and the maximum protruding length of the vane 14 protruding to the rear side compression chamber 23c are the same. Also, the maximum volume of the front side compression chamber 23b and the maximum volume of the rear side compression chamber 23c can be set to different values. As a result, according to the compressor 1 of this embodiment, a refrigerant | coolant can be appropriately compressed as a two-stage pressure | voltage rise type compressor.

  Further, in the compressor 1 of the present embodiment, the intermediate pressure refrigerant compressed in the front side compression chamber 23b constituting the large capacity side compression chamber and the intermediate pressure refrigerant sucked from the intermediate pressure refrigerant suction port 11f are merged. The refrigerant thus made is sucked into the rear side compression chamber 23c constituting the small capacity side compression chamber. Therefore, it can be applied to the refrigeration cycle 100 constituting the gas injection cycle, and the refrigeration cycle 100 can exhibit a high COP.

  Moreover, in the compressor 1 of this embodiment, the plane parts 16b, 16c, 17b, and 17c are provided in each cam surface 16a and 17a. In these flat portions 16b... 17c, the contact area (seal area) with the end of the vane 14 in the axial direction can be increased, so that the refrigerant leaks from the gaps between the vane 14 and the cam surfaces 16a and 17a. This can be suppressed.

(Second Embodiment)
In the present embodiment, an example in which the configurations of the rear bush 21c, the rear side plate 17, and the rear side cylinder 20 are changed as shown in FIG. 8 with respect to the first embodiment will be described.

  Specifically, in the present embodiment, a rear bush 21c having an outer diameter dimension equal to the outer diameter dimension of the front bush 21b is employed. Further, as the rear side plate 17, one having an outer diameter dimension smaller than the outer diameter dimension of the front side plate 16 is employed. Further, as the rear side cylinder 20, one having an inner diameter dimension smaller than the inner diameter dimension of the front side cylinder 19 is employed.

  Further, in the present embodiment, as shown in FIG. 8, as the vane 14, since the outer peripheral side of the rear side protrusion 14 c is notched, the radial dimension of the rear side protrusion 14 c is changed to the front side protrusion. The thing shorter than the dimension of the radial direction of 14b is employ | adopted.

  In other words, in the present embodiment, when viewed from the axial direction of the shaft 12, the displacement of the vane 14 in the axial direction is cut out by notching a range where the vane 14 and the rear side cylinder 20 overlap in the rear side protruding portion 14c. Is suppressed by the rear bush 21c.

  Thus, as in the first embodiment, the maximum volume (discharge capacity) of the rear side compression chamber 23c when the end surface on the other axial end side of the rotor 13 and the rear side cam surface 17a are farthest from each other is It becomes smaller than the maximum volume (discharge capacity) of the front side compression chamber 23b when the end surface on the one end side in the axial direction is farthest from the front side cam surface 16a. Other configurations and operations are the same as those in the first embodiment.

  Even if the maximum volume of the front side compression chamber 23b and the maximum volume of the rear side compression chamber 23c are set to different values as in this embodiment, the refrigerant can be appropriately compressed as a two-stage booster type compressor. Furthermore, a high COP can be exhibited in the refrigeration cycle 100 constituting the gas injection cycle. Furthermore, the same member can be employ | adopted as the front bush 21b and the rear bush 21c, and the manufacturing cost of the compressor 1 can be reduced.

(Third embodiment)
In the present embodiment, an example in which the configurations of the rear bush 21c, the rear side plate 17, and the rear side cylinder 20 are changed as shown in FIG. 9 with respect to the first embodiment will be described.

  Specifically, in the present embodiment, a rear bush 21c having an outer diameter dimension larger than the outer diameter dimension of the front bush 21b is employed. Further, as the rear side plate 17, one having an inner diameter dimension larger than the inner diameter dimension of the front side plate 16 and an outer diameter dimension smaller than the outer diameter dimension of the front side plate 16 is employed. . Further, as the rear side cylinder 20, one having an inner diameter dimension smaller than the inner diameter dimension of the front side cylinder 19 is employed.

  Moreover, in this embodiment, as shown in FIG. 8, as the vane 14, both the inner peripheral side and the outer peripheral side of the rear side protruding portion 14c are notched, so that the radial direction of the rear side protruding portion 14c is reduced. A dimension that is shorter than the dimension in the radial direction of the front protrusion 14b is employed.

  That is, in this embodiment, when viewed from the axial direction of the shaft 12, the rear protruding portion 14c cuts out a range where the vane 14 and the rear bush 21 overlap, and the vane 14 and the rear side cylinder 20 overlap. By notching the range, the displacement of the vane 14 in the axial direction is prevented from being restricted by the rear bush 21c.

  Thus, as in the first embodiment, the maximum volume (discharge capacity) of the rear side compression chamber 23c when the end surface on the other axial end side of the rotor 13 and the rear side cam surface 17a are farthest from each other is It becomes smaller than the maximum volume (discharge capacity) of the front side compression chamber 23b when the end surface on the one end side in the axial direction is farthest from the front side cam surface 16a. Other configurations and operations are the same as those in the first embodiment.

  Even if the maximum volume of the front side compression chamber 23b and the maximum volume of the rear side compression chamber 23c are set to different values as in this embodiment, the refrigerant can be appropriately compressed as a two-stage booster type compressor. Furthermore, a high COP can be exhibited in the refrigeration cycle 100 constituting the gas injection cycle.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, the front side compression chamber 23b and the rear side compression chamber 23c of the axial vane compressor 1 according to the present invention are connected in series and applied to the refrigeration cycle 100 constituting the gas injection cycle. Although an example has been described, the configuration of the axial vane compressor 1 is not limited to this.

  For example, the front housing 11b or the middle housing 11a is provided with a second discharge port for discharging the refrigerant from the intermediate pressure chamber 11g, and the middle housing 11a is provided with a second suction port communicating with the intermediate pressure refrigerant suction chamber 11m so that the intermediate pressure refrigerant is sucked. It is good also as a structure which obstruct | occludes the opening 11f and the intermediate pressure communication path 11h, and does not connect the front side compression chamber 23b and the rear side compression chamber 23c.

  According to this, the front side compression chamber 23b and the rear side compression chamber 23c are made to be mutually independent compression mechanisms, and fluids of different types, different flow rates, or different densities are flowed in, and each fluid is appropriately compressed. You can also.

  Further, for example, the intermediate pressure refrigerant inlet 11f may be closed to prevent the intermediate pressure refrigerant from flowing into the housing from the outside. According to this, since it can be used in the same manner as a single-stage booster type compressor and the two compression chambers are connected in series, the pressure difference between the discharge refrigerant pressure and the suction refrigerant pressure (high-low pressure difference) ) Becomes higher, the compression efficiency can be improved.

  (2) In the above-described embodiment, the example in which the axial vane compressor 1 according to the present invention is applied to the refrigeration cycle 100 has been described. However, the refrigeration cycle to which the axial vane compressor 1 of the present invention can be applied is It is not limited to.

  For example, a compressor, a radiator that exchanges heat between the high-pressure refrigerant discharged from the compressor and outdoor air (outside air) to dissipate the high-pressure refrigerant, and a refrigerant that flows out of the radiator is reduced in pressure until it becomes an intermediate-pressure refrigerant. A high-stage expansion valve, a gas-liquid separator that separates the gas-liquid of the intermediate-pressure refrigerant decompressed by the high-stage expansion valve, and the liquid-phase refrigerant separated by the gas-liquid separator becomes a low-pressure refrigerant And a low-stage expansion valve that depressurizes to a low pressure, and an evaporator that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing out of the low-stage expansion valve and the indoor blowing air, and separated by a gas-liquid separator The present invention may be applied to a gas injection cycle in which gas-phase refrigerant is sucked into the intermediate-pressure refrigerant suction port 11f of the compressor and low-pressure refrigerant flowing out of the evaporator is sucked into the low-pressure refrigerant suction port of the compressor.

  Furthermore, as described above, the intermediate pressure refrigerant suction port 11f may be closed and applied to a normal refrigeration cycle.

  (3) In the above-described embodiment, the example in which the axial vane compressor 1 according to the present invention is applied to the refrigeration cycle 100 for an air conditioner has been described, but the application of the axial vane compressor 1 according to the present invention is applied to this example. It is not limited. That is, the axial vane type compressor 1 of the present invention can be applied to a wide range of uses as a compressor that compresses various fluids.

  Furthermore, in the above-described embodiment, the radiator 2 is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 4 is used as a use-side heat exchanger that cools the blown air. Axial according to the present invention is a heat pump cycle in which the evaporator 4 is configured as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 2 is configured as an indoor heat exchanger that heats a heated fluid such as air or water. The vane compressor 1 may be applied.

  (4) In the above-described embodiment, the compression chambers 23b and 23c are connected to the axial end surfaces of the rotor 13, the flat surfaces of the adjacent vanes 14, the cam surfaces 16a and 17a, the inner peripheral surfaces of the side cylinders 19 and 20, In addition, the example in which the bushes 21b and 21c are formed by the space surrounded by the outer peripheral surface has been described, but the formation of the compression chambers 23b and 23c is not limited thereto.

  For example, as in the second embodiment, the outer diameters of the bushes 21b and 21c are equal, and leakage from the gap between the shaft 12 and the bearings 22b and 22c can be suppressed by a mechanical seal or the like. If so, the bushes 21b and 21c may be eliminated, and the compression chambers 23b and 23c may be formed by the outer peripheral surface of the shaft 12.

  (5) In the refrigeration cycle 100 of the above-described embodiment, the example in which the subcritical refrigeration cycle in which the pressure of the refrigerant discharged from the compressor 1 does not exceed the critical pressure of the refrigerant has been described. For example, carbon dioxide or the like is used as the refrigerant. Then, a supercritical refrigeration cycle in which the pressure of the refrigerant discharged from the compressor 1 exceeds the critical pressure of the refrigerant may be configured.

12 Rotating shaft 13 Rotor 13a Slit groove 14 Vane 14b, 14c Front side protrusion, Rear side protrusion 16, 17 Front side plate, Rear side plate 16a, 17a Front side cam surface, Rear side cam surface 18, 19, 20 Middle cylinder , Front side cylinder, rear side cylinder 23b, 23c front side compression chamber, rear side compression chamber

Claims (5)

A rotating shaft (12) that rotates by being transmitted with a rotational driving force;
A plurality of slit grooves (13a) extending in the axial direction of the rotating shaft (12) are formed on the outer peripheral surface, and a cylindrical rotor (13) coaxially connected to the rotating shaft (12);
A plurality of vanes (14) formed in a flat plate shape extending parallel to the radial direction and the axial direction of the rotating shaft (12), and slidably fitted in the slit groove (13a);
As the vane (14) is rotationally displaced around the rotary shaft (12), the vane (14) is displaced in the axial direction by coming into contact with the end of the vane (14) on one end side in the axial direction. A front side plate (16) having a front cam surface (16a) formed thereon;
The vane (14) is brought into contact with the end portion on the other axial end side of the vane (14), and as the vane (14) is rotationally displaced around the rotating shaft (12), the vane (14) is moved in the axial direction. A rear side plate (17) formed with a rear cam surface (17a) to be displaced;
A cylindrical space is formed inside, and cylinders (18, 19, 20) disposed on the outer peripheral side of the rotor (13), the front side plate (16) and the rear side plate (17),
A space surrounded by an end face on one axial end side of the rotor (13), a flat face of the adjacent vane (14), the front cam face (16a), and an inner peripheral face of the cylinder (18-20). To form a front compression chamber (23b) for compressing fluid,
Surrounded by the end face on the other end side in the axial direction of the rotor (13), the flat face of the adjacent vane (14), the rear cam face (17a), and the inner peripheral face of the cylinder (18-20). A rear side compression chamber (23c) for compressing fluid is formed by the space,
The axial vane type compressor, wherein the maximum volume of the front side compression chamber (23b) and the maximum volume of the rear side compression chamber (23c) are different values.   Of the vane (14), the shape of the portion protruding from the rotor (13) toward the front side plate (16) and the shape protruding from the rotor (13) toward the rear side plate (17) The axial vane type compressor according to claim 1, wherein the shapes of the parts are different.   A radial dimension of a portion of the vane (14) protruding from the rotor (13) toward the front side plate (16) when viewed from the axial direction of the rotary shaft (12), and The axial vane type compressor according to claim 2, characterized in that the radial dimension of the portion projecting from the rotor (13) toward the rear side plate (17) is different. Of the front-side compression chamber (23b) and the rear-side compression chamber (23c), the side with the largest maximum volume is the large-capacity side compression chamber (23b), and the side with the smaller maximum volume is the small-capacity side compression chamber (23c). And when
The axial pressure according to any one of claims 1 to 3, wherein the intermediate pressure fluid discharged from the large-capacity side compression chamber (23b) is sucked into the small-capacity side compression chamber (23c). Vane type compressor.   Further, the fluid obtained by joining the intermediate pressure fluid sucked from the outside and the intermediate pressure fluid discharged from the large capacity side compression chamber (23b) is sucked into the small capacity side compression chamber (23c). The axial vane type compressor according to claim 4, wherein the compressor is an axial vane type compressor.

Images