JPWO2019043741A1 - Compressor - Google Patents

Abstract

The compressor has a fixed scroll having a base plate portion and a spiral wrap portion formed on the base plate portion, and an orbiting scroll having a base plate portion and a spiral wrap portion formed on the base plate portion. The fixed scroll has at least one subport for discharging the working gas or at least one injection port for injecting the working fluid in a liquid phase, and the orbiting scroll has a spiral wrap portion. A tip seal is provided at the tip along the spiral direction, and is provided with a tip seal in contact with the base plate portion of the fixed scroll facing the tip seal. , Are arranged on the edge side.

Description

  The present invention relates to a compressor for compressing a working gas.

  2. Description of the Related Art Conventionally, a scroll compressor has been known as one of compressors used for a refrigerator or an air conditioner. The scroll compressor has a fixed scroll and an orbiting scroll, and the orbiting scroll performs a revolving orbiting motion with respect to the fixed scroll. The fixed scroll and the orbiting scroll are members in which a spiral wrap portion is formed on surfaces facing each other, and a compression chamber is formed by both combined wrap portions. Then, the scroll compressor changes the internal volume of the compression chamber by swinging the orbiting scroll, and compresses the working gas flowing into the compression chamber. A seal member called a tip seal is fitted to the tip surface of the spiral wrap portion in the fixed scroll and the orbiting scroll. The tip seal rises due to the back pressure during the operation of the compressor, and fills a gap between the tip surface of the wrap portion and the base plate surface of the other scroll, thereby preventing leakage of working gas between the adjacent compression chambers. Plays the function of preventing.

  Patent Document 1 discloses a scroll compressor in which a notch is provided in a portion of a tip seal that interferes with a subport to prevent the tip seal from interfering with the subport and to prevent wear of the tip seal due to catching on the subport. .

JP-A-61-41882

  The sub-port formed in the fixed scroll has a function of preventing the occurrence of power loss due to over-compression by discharging the working gas from the middle of the scroll during operation under a low compression ratio condition. In the compressor, as the diameter of the subport is larger, the flow path resistance is smaller, and the effect of reducing power loss due to overcompression is greater. However, since the sub-port is provided at a position approaching the tip seal provided on the orbiting scroll, the diameter of the sub-port is made too large, and if the sub-port straddles the tip seal, the pressure between the adjacent compression chambers through the sub-port is increased. This will cause leakage of the working gas. Therefore, it is necessary to design the diameter of the subport as large as possible without crossing the tip seal.

  The scroll compressor disclosed in Patent Literature 1 does not have the effect of enlarging the seal width by the tip seal, and reduces the diameter of the subport or the diameter of the injection port by (wrap part width / 2 + tip seal width / 2). Cannot be too large. Therefore, a sufficient flow passage area cannot be ensured in the subport, and an excessive compression loss may occur in the compressor. In addition, the injection port cannot secure a sufficient flow passage area, and the compressor may have an insufficient discharge flow rate, thereby increasing the discharge temperature.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a compressor that secures a large diameter of a subport or a diameter of an injection port even when a tip seal is used.

  The compressor according to the present invention includes a fixed scroll having a base plate portion and a spiral wrap portion formed on the base plate portion, and an orbiting scroll including a base plate portion and a spiral wrap portion formed on the base plate portion. The fixed scroll has at least one subport for discharging the working gas or at least one injection port for injecting a liquid-phase working fluid. A tip seal is provided at the tip of the spiral wrap along the spiral direction and is in contact with the base plate of the fixed scroll facing the tip seal.The tip seal has a portion approaching the subport or the injection port in the width direction of the spiral wrap. It is arranged on the edge side with respect to the center.

  According to the present invention, in the tip seal, a portion approaching the subport or the injection port is arranged on the edge side with respect to the center in the width direction of the spiral wrap portion. That is, the tip seal is disposed on the side away from the subport or the injection port with respect to the center of the swinging spiral wrap portion. For this reason, the compressor can secure a large seal width by the tip seal and reduce the diameter of the sub port or the injection port as compared with the case where the tip seal is formed in one involute shape and arranged at the center of the swing wrap portion. Can be designed large.

1 is an axial sectional view showing a compressor according to Embodiment 1 of the present invention. It is a horizontal sectional view showing the shape of an orbiting scroll, a fixed scroll, and a tip seal in a prior art. FIG. 3 is an enlarged view showing a swing scroll and a fixed scroll in which the swing scroll of FIG. 2 has moved. FIG. 4 is a vertical sectional view showing a relationship between a tip seal and a subport or an injection port in FIG. 3. FIG. 4 is a vertical cross-sectional view of a compression section when a tip seal does not contact a fixed scroll. FIG. 3 is an axial sectional view showing shapes of an orbiting scroll, a fixed scroll, and a tip seal in the compressor according to Embodiment 1 of the present invention. FIG. 9 is an axial sectional view showing shapes of an orbiting scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 2 of the present invention. FIG. 10 is an axial sectional view showing shapes of an orbiting scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 3 of the present invention. FIG. 14 is an axial sectional view showing shapes of an orbiting scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 4 of the present invention. FIG. 13 is an axial sectional view showing shapes of an orbiting scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 5 of the present invention.

  Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings and the like. In the following drawings including FIG. 1, the relative dimensional relationships, shapes, and the like of the components may be different from actual ones. Further, in the following drawings, the same reference numerals denote the same or corresponding components, and this is common in the entire text of the specification. In addition, in order to facilitate understanding, terms indicating directions (for example, “up,” “down,” “right,” “left,” “front,” “back,” and the like) are used as appropriate, For convenience of description, such description is merely provided, and does not limit the arrangement and orientation of the device or the component.

Embodiment 1 FIG.
[Compressor 100]
FIG. 1 is an axial sectional view showing a compressor 100 according to Embodiment 1 of the present invention. The compressor 100 is a scroll compressor that sucks and compresses a refrigerant circulating in a refrigeration cycle, and discharges the refrigerant in a state of high temperature and high pressure. As shown in FIG. 1, the compressor 100 has a shell 20, a motor 30, a compressor 40, and a shaft 50. The compressor 100 is a low-pressure shell-type compressor.

[Shell 20]
The shell 20 forms an outer shell of the compressor 100 and has pressure resistance. The shell 20 has a bottomed cylindrical shape, and includes a lower shell 20a located at the bottom, a central shell 20b mounted on the lower shell 20a and formed in a cylindrical shape, and an upper shell 20c closing an upper part of the central shell 20b. Have. Shell 20 has an oil sump 21 for storing oil at the bottom. An oil pump 23 disposed in an oil reservoir 21 of the shell 20 is accommodated in a lower portion of the shell 20. The oil pump 23 is attached to one end of the shaft 50, sucks oil stored in the oil sump 21 of the shell 20, and supplies the oil to an oil supply passage 50 a in the shaft 50. The oil supplied to the oil supply passage 50 a is supplied to a bearing portion inside the compressor 100 and the Oldham ring 41. This oil lubricates and cools the bearing portion and the Oldham ring 41. A suction pipe 27 is provided on a side of the shell 20. The suction pipe 27 is a pipe that sucks working gas into the inside of the shell 20. A discharge pipe 28 is provided above the shell 20. The discharge pipe 28 is a pipe that discharges the working gas to the outside of the shell 20. The muffler 29 is provided above a fixed scroll 60 described later, and suppresses pulsation of the working gas discharged from the discharge port 65 and the sub port 62.

  The frame 25 is provided above the motor 30 inside the shell 20 and is fixed to the shell 20. The orbiting scroll 70 and the fixed scroll 60 are mounted on the frame 25 in a state where the spiral wrap portions are combined so as to mesh with each other. In the first embodiment, an example in which the fixed scroll 60 is fixed to the frame 25 will be described. However, the fixed scroll 60 may be configured to be fixed to the shell 20 without being fixed to the frame 25. The frame 25 rotatably supports the shaft 50 via a main bearing 54. A suction port 25a is formed in the frame 25, and the working gas flows into the compression section 40 through the suction port 25a. The sub frame 26 is provided below the motor 30 inside the shell 20 and is fixed to the shell 20. The sub-frame 26 rotatably supports the shaft 50 via a sub-bearing 55.

  The oil drain pipe 24 is a pipe that connects a space between the frame 25 and the orbiting scroll 70 and a space between the frame 25 and the sub-frame 26. The oil drain pipe 24 allows excess oil among the oil flowing in the space between the frame 25 and the orbiting scroll 70 to flow out into the space between the frame 25 and the sub-frame 26. The oil that has flowed into the space between the frame 25 and the sub-frame 26 passes through the sub-frame 26 and returns to the oil sump 21.

[Motor 30]
The motor 30 rotates the shaft 50. The motor 30 is provided inside the shell 20 and is installed between the frame 25 and the sub-frame 26. The motor 30 has a rotor 31 and a stator 32. The rotor 31 is provided on the inner peripheral side of the stator 32, and is attached to the shaft 50. The rotor 31 rotates the shaft 50 by rotating itself. Stator 32 is fixed to shell 20 by shrink fitting or the like. Stator 32 generates a magnetic field by electric power supplied from an inverter (not shown), and rotates rotor 31.

[Compression unit 40]
The compression section 40 is provided inside the shell 20 and is driven by the motor 30 to compress the working gas. The compression section 40 is housed in the frame 25 and has a fixed scroll 60 and an orbiting scroll 70. The fixed scroll 60 is fixed inside the shell 20, and the fixed scroll 60 is formed with a discharge port 65 and a sub port 62 for discharging the compressed working gas. The orbiting scroll 70 makes a revolving orbiting motion with respect to the fixed scroll 60, and the rotation is restricted by the Oldham ring 41. The fixed scroll 60 and the orbiting scroll 70 have a spiral fixed spiral wrap portion 61 and an orbiting spiral wrap portion 71, which will be described later, formed on surfaces facing each other. The compression part 40 forms a compression chamber in a space where the fixed spiral wrap part 61 and the swing spiral wrap part 71 mesh. When the orbiting scroll 70 is swung by the rotation of the shaft portion 50, the working gas is compressed in the compression chamber. The detailed configuration of the compression unit 40 will be described later.

  The Oldham ring 41 is an annular member attached to the orbiting scroll 70, and regulates the rotation of the orbiting scroll 70. The Oldham ring 41 is attached to an Oldham groove 41 a formed on the thrust lower surface of the orbiting scroll 70. The slider 42 is a cylindrical member attached to the outer peripheral surface of the upper part of the shaft part 50, and is located on the inner surface of the lower part of the orbiting scroll 70. That is, the orbiting scroll 70 is attached to the shaft 50 via the slider 42, and the orbiting scroll 70 rotates with the rotation of the shaft 50. A swing bearing 43 is provided between the swing scroll 70 and the slider 42. The sleeve 44 is a cylindrical member provided between the frame 25 and the main bearing 54, and is a member for absorbing a relative inclination between the main bearing 54 and the shaft 50.

[Shaft 50]
The shaft 50 is supported by the frame 25. The main bearing 54 provided between the shaft 50 and the frame 25 has a bearing structure made of a sliding bearing made of, for example, a copper-lead alloy, and rotatably supports the shaft 50. Although the case where the main bearing 54 is formed of a sliding bearing is illustrated, the shaft portion 50 may be supported by another known bearing structure. The shaft portion 50 has an oil supply passage 50a formed therein, connects the motor 30 and the compression portion 40, and transmits the rotational force of the motor 30 to the compression portion 40.

  A first balancer 52 is attached to the shaft 50. The first balancer 52 is located between the frame 25 and the rotor 31. The first balancer 52 cancels the imbalance caused by the orbiting scroll 70 and the slider 42. The first balancer 52 is housed in a balancer cover 52a. The second balancer 53 is attached to the shaft 50 via the rotor 31. The second balancer 53 is located between the rotor 31 and the sub frame 26 and is attached to the lower surface of the rotor 31. The second balancer 53 cancels the imbalance caused by the orbiting scroll 70 and the slider 42.

[Details of compression unit 40]
Next, details of the compression unit 40 will be described in detail. The compression section 40 has the fixed scroll 60 and the orbiting scroll 70 as described above. The fixed scroll 60 is fixed inside the shell 20, and has an outer peripheral edge placed on an upper portion of the frame 25. The fixed scroll 60 has a fixed spiral base plate portion 64 and a fixed spiral wrap portion 61 formed on the fixed spiral base plate portion 64. A discharge port 65 and a sub port 62 are formed in the fixed scroll base plate portion 64 of the fixed scroll 60. The working gas compressed in the compression chamber is discharged through the discharge port 65 and the sub port 62. Alternatively, an injection port 63 may be formed in the fixed scroll 60 instead of the sub port 62. Intermediate pressure working gas discharged from the compressor 100 and passed through an injection circuit (not shown) is introduced into the compression chamber through the injection port 63. The orbiting scroll 70 has an orbiting spiral base plate 74 and an orbiting spiral wrap 71 formed on the orbiting spiral base plate 74.

  Discharge of the compressed gas from the subport 62 is performed under operating conditions with a small compression ratio. Before the compressed gas reaches the center of the compression chamber, it passes through the subport 62 and is bypassed into the upper shell 20c, so that the compressor 100 can reduce power loss due to excessive compression.

  The injection port 63 is used to inject a liquid-phase working fluid into the compression chamber during operation under a condition of a high compression ratio. The injection port 63 has a function of lowering the temperature of the discharge gas and preventing the fixed scroll 60 and the orbiting scroll 70 from being damaged by thermal expansion.

  FIG. 2 is a horizontal sectional view showing the shapes of the orbiting scroll 70, the fixed scroll 60, and the tip seal 80 in the prior art. FIG. 3 is an enlarged view showing the orbiting scroll 70 and the fixed scroll 60 in which the orbiting scroll 70 in FIG. The positions of these horizontal cross sections correspond to the line AA in the compressor 100 of FIG. In addition, in the following drawings, the position of the discharge port 65, the sub port 62 or the injection port 63 formed in the fixed scroll base plate portion 64 is also shown in plan view of the compressor. The subport 62a and the subport 62b described below are collectively referred to as the subport 62, and the injection port 63a and the injection port 63b are collectively referred to as the injection port 63. First, the configurations of the sub port 62 and the injection port 63 common to the compressor 100 will be described with reference to FIGS. As shown in FIG. 2 and FIG. 3, a sub-port 62 a is formed in the compression chamber 40 a on the outward surface side of the fixed scroll 60 in the stationary scroll base plate portion 64 of the fixed scroll 60, and the compression on the inward surface side of the fixed scroll 60 is performed. A sub port 62b is formed in the chamber 40b. The sub-port 62a and the sub-port 62b are arranged at a position where a pair of the compression chamber 40a on the outer side of the fixed scroll and the compression chamber 40b on the inner side of the fixed scroll is provided. When the fixed scroll 60 is formed with an injection port 63 instead of the sub port 62, an injection port 63 is formed instead of the sub port 62 of FIGS. In this case, in the fixed scroll base plate portion 64 of the fixed scroll 60, an injection port 63a is formed in the compression chamber 40a on the outward surface side of the fixed scroll 60, and the injection port 63b is formed in the compression chamber 40b on the inward surface side of the fixed scroll 60. Are formed. The injection port 63a and the injection port 63b are arranged at a position that is a pair of the compression chamber 40a on the outer side of the fixed scroll and the compression chamber 40b on the inner side of the fixed scroll. The number of the subports 62 may be one, or a plurality of pairs of subports 62 may be provided. Similarly, the number of the injection ports 63 may be one, or a plurality of pairs of the injection ports 63 may be provided.

  Next, the tip seal 80 will be described. A tip seal fitting groove 81 having the same shape as the tip seal 80 is formed on the tip end surface of the wrap of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 80 fits into the tip seal fitting groove 81. Have been. The tip seal 80 of the orbiting scroll 70 is arranged at the tip of the orbiting spiral wrap 71 along the direction of the spiral, and comes into contact with the fixed scroll base plate 64 of the fixed scroll 60 facing the same. A tip seal 80 (not shown) of the fixed scroll 60 is disposed at the tip of the fixed scroll wrap 61 along the spiral direction, and is in contact with the swinging scroll base plate 74 of the swing scroll 70 facing the same. The tip seal 80 slides while being pressed against the fixed scroll base plate 64 during the operation of the compressor 100, so that the gap between the swinging spiral wrap 71 and the fixed scroll base plate 64, and the fixed spiral wrap The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 80 slides while being pressed against the oscillating swirl base plate 74 during operation of the compressor 100, so that the gap between the fixed swirl wrap part 61 and the oscillating swirl base plate 74 and the fixed state. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 and the injection port 63 are provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approach the tip seal 80 provided on the tip end surface of the oscillating scroll 70. In order to ensure the sealing performance of the tip seal 80, the diameter of the sub port 62 or the injection port 63 needs to be set within a range that does not completely straddle the tip seal 80.

  Here, dimensional restrictions when providing the sub port 62 or the injection port 63 will be described. Since the sub port 62 or the injection port 63 is disposed at a position overlapping the tip seal 80 of the orbiting scroll 70, the sub port 62 or the injection port 63 must be completely sized so as not to straddle the tip seal 80 of the orbiting scroll 70. There is. In FIG. 3, δ is a contact range between the tip seal 80 and the fixed scroll 60, and is a seal width between the tip seal 80 and the fixed scroll 60. That is, the compression unit 40 needs to set the diameter of the sub port 62 or the injection port 63 in the fixed scroll 60 so as to satisfy the seal width δ> 0.

  FIG. 4 is a vertical sectional view showing the relationship between the tip seal 80 and the sub port 62 or the injection port 63 of FIG. FIG. 5 is a vertical sectional view of the compression section 40 when the tip seal 80 does not contact the fixed scroll 60. FIG. 4 is a vertical cross-sectional view of the compression section 40 when the seal width δ by the tip seal 80 and the fixed scroll 60 is formed such that the seal width δ> 0. At this time, the compression section 40 does not leak from the high-pressure chamber 46 to the low-pressure chamber 45 because there is a seal width δ at which the tip seal 80 of the orbiting scroll 70 and the fixed scroll base plate section 64 come into contact. The upper limit of the seal width δ is the width γ of the tip seal 80. FIG. 5 is a vertical cross-sectional view of the compression section 40 when the seal width δ formed by the tip seal 80 and the fixed scroll 60 is set so that the seal width δ <0. At this time, since there is no seal width δ at which the tip seal 80 of the orbiting scroll 70 contacts the fixed scroll base plate portion 64, the high-pressure chamber 46 and the low-pressure chamber 45 communicate with each other through the subport 62, and Leakage of the working gas into the low-pressure chamber 45 occurs. Therefore, the diameter of the sub-port 62 or the injection port 63 can be increased only in a range satisfying δ> 0, and in order to provide a large diameter of the sub-port 62 or the injection port 63, the tip seal 80 of the orbiting scroll 70 must be provided. It is necessary to devise the shape.

  FIG. 6 is an axial sectional view showing shapes of the orbiting scroll 70, the fixed scroll 60, and the tip seal 82 in the compressor 100 according to Embodiment 1 of the present invention. A tip seal fitting groove 81 having the same shape as the tip seal 82 is formed on the wrap tip surface of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 82 is fitted into the tip seal fitting groove 81. Have been. The tip seal 82 of the orbiting scroll 70 is arranged at the tip of the orbiting spiral wrap 71 along the spiral direction, and comes into contact with the fixed spiral base plate portion 64 of the fixed scroll 60 facing the same. A tip seal 82 (not shown) of the fixed scroll 60 is disposed at the tip of the fixed scroll wrap 61 along the spiral direction, and is in contact with the swing scroll base plate 74 of the swing scroll 70 facing the spiral scroll wrap 61. The tip seal 82 slides while being pressed against the fixed scroll base plate 64 during the operation of the compressor 100, so that the gap between the swinging spiral wrap 71 and the fixed scroll base plate 64, and the fixed spiral wrap The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 82 slides while being pressed against the oscillating swirl base plate 74 during operation of the compressor 100, so that the gap between the fixed swirl wrap part 61 and the oscillating swirl base plate 74 and the fixed state. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 or the injection port 63 is provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approaches the tip seal 82 provided on the wrap tip surface of the orbiting scroll 70. In order to ensure the sealing property of the tip seal 82, the diameter of the sub port 62 or the injection port 63 needs to be set within a range where the tip seal 82 is not completely straddled.

  As shown in FIG. 6, the tip seal 82 is constituted by a plurality of curves having different curvatures, and includes three curves of a first curved portion 82a, a second curved portion 82b, and a third curved portion 82c. The parts are joined together to form an integral part. In FIG. 6, the tip seal 82 is illustrated as having a cut in order to clearly show the boundary of the curve, but the tip seal 82 is an integral body without a cut. That is, in the tip seal 82, a plurality of curves having different curvatures are continuously formed. In the tip seal 82, the portion approaching the sub port 62 or the injection port 63 is located on the outer peripheral edge 71 b side and the inner peripheral edge 71 c side with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. Are located.

  The tip seal 82 has a first curved portion 82a in which the portion approaching the subport 62a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71b side with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. Having. Alternatively, in the tip seal 82, the portion approaching the injection port 63 a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71 b side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has a curved portion 82a. The first curved portion 82a is formed of an involute curve having the same curvature as the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The tip seal 82 has a second curved portion where the portion approaching the subport 62 b on the inward surface side of the fixed scroll 60 passes through the inner peripheral edge 71 c side with respect to the widthwise center 71 a of the orbiting spiral wrap portion 71. 82b. Alternatively, in the tip seal 82, the portion approaching the injection port 63 b on the inward surface side of the fixed scroll 60 passes through the inner peripheral edge 71 c side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has two curved portions 82b. The second curved portion 82b is formed of an involute curve having the same curvature as the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The boundary between the first curved portion 82a and the second curved portion 82b is connected by a third curved portion 82c formed into a smooth curve such as an involute curve having a curvature larger than that of the orbiting scroll 70. In the compressor 100 according to the first embodiment, the tip seal 82 is formed of three curved portions, but the number of curved portions forming the tip seal 82 is changed according to the number of subports 62 or injection ports 63. It goes without saying that it is good. Note that the shape of the tip seal 82 of the fixed scroll 60 is formed by an involute curve having the same curvature as the fixed spiral wrap portion 61 of the fixed scroll 60, and the center 71a in the width direction of the fixed spiral wrap portion 61 of the fixed scroll 60, as before. May be arranged.

  As described above, the tip seal 82 of the compressor 100 is configured such that the portion approaching the sub port 62 or the injection port 63 is located on the outer peripheral edge 71 b side with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It is arranged on the inner edge 71c side. That is, the portions of the tip seal 82 approaching the subport 62a on the outward surface of the fixed scroll 60 and the subport 62b on the inward surface of the fixed scroll 60 are separated from the subport 62 with respect to the center 71a of the orbiting spiral wrap 71, respectively. Located on the side. Therefore, the compressor 100 can secure the seal width δ larger than the case where the tip seal 82 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the The diameter can be designed to be large.

  Specifically, when the tip seal 82 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the subport 62 is set to "(wrap portion) in order to satisfy the seal width δ> 0. Width / 2) + (tip seal width / 2) ”. On the other hand, in the compressor 100, the tip seal 82 is integrally formed by joining three curved portions of the first curved portion 82a, the second curved portion 82b, and the third curved portion 82c. Therefore, it is possible to enlarge the diameter of the subport 62 beyond this restriction value.

  Further, the injection port 63 of the compressor 100 having the injection port 63 instead of the sub port 62 can be similarly designed to be large. In the compressor 100, the injection port 63a of the tip seal 82 and the portion approaching the injection port 63b are respectively disposed on the side away from the injection port 63 with respect to the center 71a of the swing spiral wrap portion 71. Therefore, the compressor 100 can secure the seal width δ larger than the case where the tip seal 82 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the injection port 63 Can be designed with a large diameter.

  Specifically, when the tip seal 82 is disposed at the center 71a of the tip end surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the injection port 63 must be changed to "(wrap) in order to satisfy the seal width δ> 0. (Part width / 2) + (tip seal width / 2) ”. In the compressor 100, the tip seal 82 is integrally formed by joining three curved portions of the first curved portion 82a, the second curved portion 82b, and the third curved portion 82c having the above configuration. Therefore, the diameter of the injection port 63 can be increased to a value larger than the restriction value.

  Accordingly, the resistance of the compressor 100 when the working gas is discharged from the sub port 62 is reduced, and the performance of the compressor 100 can be improved. Further, when the injection port 63 is formed instead of the sub port 62, the compressor 100 can increase the flow rate of the liquid-phase working fluid to be injected, and can more efficiently lower the discharge temperature.

  Further, for example, when a notch is provided in the tip seal as in the related art, gas leaks from the notch to between adjacent compression chambers, and the performance of the compressor may be significantly reduced. Furthermore, the strength of the tip seal may decrease due to stress concentration on the notch of the tip seal. In the compressor 100, the chip seal 82 is disposed at a position away from the sub port 62 or the injection port 63, and the chip seal 82 is not provided with a notch. Therefore, in the compressor 100, gas leakage does not occur between the compression chambers, and the strength of the tip seal 82 does not decrease due to stress concentration.

  Further, in the conventional compressor, the tip seal 80 is formed into a spiral shape with a hard resin, and the tip seal 80 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 are fixed to the orbiting spiral wrap portion 71, respectively. The spiral wrap portion 61 is disposed at the center 71a of the distal end surface. Therefore, in the conventional compressor, there is a possibility that the tip seal 80 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 are attached alternately, and an assembly failure may occur. On the other hand, in the compressor 100, the tip seal 82 is integrally formed by joining three curved portions of the first curved portion 82a, the second curved portion 82b, and the third curved portion 82c having the above configuration. Have been. The compressor 100 forms the tip seal 80 of the fixed scroll 60 in the form of an involute curve as in the past, and when the tip seal 80 is disposed at the center 71 a of the tip end surface of the fixed spiral wrap portion 61, the tip seal 80 of the fixed scroll 60 and the orbiting scroll 70 The shape of the tip seal 82 is different. Therefore, the compressor 100 can prevent the tip seal 82 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled alternately by mistake.

  Further, since the tip seal 82 of the compressor 100 smoothly connects a plurality of curves to each other, the fitting groove of the tip seal 82 can be processed at a time with a single stroke in the orbiting scroll 70, and excellent processing is achieved. Nature can be secured.

Embodiment 2 FIG.
FIG. 7 is an axial sectional view showing the shapes of the orbiting scroll 70, the fixed scroll 60, and the tip seal 83 in the compressor 110 according to Embodiment 2 of the present invention. Portions having the same configuration as the compressor 100 of FIGS. The compressor 110 is the same as the compressor 100 except that the configuration of the tip seal 83 differs from the configuration of the tip seal 82 of the compressor 100.

  A tip seal fitting groove 81 having the same shape as the tip seal 83 is formed on the wrap tip surface of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 83 fits into the tip seal fitting groove 81. Have been. The tip seal 83 of the orbiting scroll 70 is disposed at the tip of the orbiting spiral wrap 71 along the spiral direction, and is in contact with the fixed spiral base plate 64 of the fixed scroll 60 facing the same. The tip seal 83 (not shown) of the fixed scroll 60 is arranged at the tip of the fixed scroll wrap portion 61 along the spiral direction, and comes into contact with the swinging scroll base plate portion 74 of the swing scroll 70 facing the same. The tip seal 83 slides while being pressed against the fixed scroll base plate 64 during the operation of the compressor 110, so that the gap between the swinging spiral wrap 71 and the fixed scroll base plate 64, and the fixed spiral wrap The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 83 slides while being pressed against the oscillating swirl plate 74 during the operation of the compressor 110, so that the gap between the fixed swirl wrap portion 61 and the oscillating swirl plate 74 is fixed. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 or the injection port 63 is provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approaches the tip seal 83 provided on the tip end surface of the oscillating scroll 70. In order to ensure the sealing property of the tip seal 83, the diameter of the sub port 62 or the injection port 63 needs to be set within a range where the tip seal 83 is not completely straddled.

  As shown in FIG. 7, in the compressor 110, the tip seal 83 is configured by a plurality of curves having different curvatures, and the two curved portions of the first curved portion 83a and the second curved portion 83b are combined. They are integrally connected to each other. In FIG. 7, the tip seal 83 is illustrated as having a break in order to clearly show the boundary between the curves, but the boundary between the two curves is not divided, and the tip seal 83 is an integral body without a break. is there. That is, in the tip seal 83, a plurality of curves having different curvatures are continuously formed. In the tip seal 83, the portion approaching the sub port 62 or the injection port 63 is located on the outer peripheral edge 71b side and the inner peripheral edge 71c side with respect to the center 71a in the width direction of the swing spiral wrap portion 71. Are located.

  The tip seal 83 has a first curved portion 83a in which a portion approaching the subport 62a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71b side with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. Having. Alternatively, in the tip seal 83, the portion approaching the injection port 63 a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71 b side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has a curved portion 83a. The first curved portion 83a is formed of an involute curve having the same curvature as the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The tip seal 83 is formed of an involute curve having a curvature larger than that of the orbiting scroll 70, and has a second curved portion 83b arranged from the inside of the orbiting spiral wrap portion 71 as approaching the center of the spiral. In the second curved portion 83b of the tip seal 83, the portion approaching the subport 62b on the inward surface side of the fixed scroll 60 is closer to the inner peripheral edge portion 71c than the widthwise center 71a of the orbiting spiral wrap portion 71. Pass through. Alternatively, the second curved portion 83b of the tip seal 83 is such that the portion approaching the injection port 63b on the inward surface side of the fixed scroll 60 has an inner peripheral edge with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. It passes through the part 71c side.

  In the compressor 110 according to the second embodiment, the tip seal 83 is constituted by two curved portions, but the number of curved portions constituting the tip seal 83 is changed according to the number of the subports 62 or the injection ports 63. It goes without saying that it is good. The shape of the tip seal 83 of the fixed scroll 60 is formed by an involute curve having the same curvature as that of the fixed spiral wrap portion 61 of the fixed scroll 60, and the center 71a in the width direction of the fixed spiral wrap portion 61 of the fixed scroll 60, as before. May be arranged.

  As described above, in the tip seal 83 of the compressor 110, the portion approaching the sub-port 62 or the injection port 63 is located at the outer peripheral edge portion 71b side with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It is arranged on the inner edge 71c side. That is, the portions of the tip seal 83 approaching the subport 62a on the outward surface side of the fixed scroll 60 and the subport 62b on the inward surface side of the fixed scroll 60 are separated from the subport 62 with respect to the center 71a of the orbiting spiral wrap 71, respectively. Located on the side. Therefore, the compressor 110 can secure the seal width δ larger than the case where the tip seal 83 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the The diameter can be designed to be large.

  Specifically, when the tip seal 83 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the subport 62 is set to “(wrap portion) in order to satisfy the seal width δ> 0. Width / 2) + (tip seal width / 2) ”. On the other hand, in the compressor 110, the tip seal 83 is integrally formed by joining two curved portions of the first curved portion 83a and the second curved portion 83b. The diameter of 62 can be enlarged.

  Further, the injection port 63 of the compressor 110 having the injection port 63 instead of the subport 62 can be similarly designed to be large. In the compressor 110, the injection port 63a of the tip seal 83 and the portion approaching the injection port 63b are respectively disposed on the side away from the injection port 63 with respect to the center 71a of the swing spiral wrap portion 71. Therefore, the compressor 110 can secure the seal width δ larger than the case where the tip seal 83 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the injection port 63 Can be designed with a large diameter.

  Specifically, when the tip seal 83 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the injection port 63 must be changed to “(wrap) in order to satisfy the seal width δ> 0. (Part width / 2) + (tip seal width / 2) ”. In the compressor 110, since the tip seal 83 is integrally formed by joining the two curved portions of the first curved portion 83a and the second curved portion 83b having the above-described configuration, the injection is more than the restriction value. The diameter of the port 63 can be enlarged.

  Thus, the resistance of the compressor 110 when the working gas is discharged from the subport 62 is reduced, and the performance of the compressor 110 can be improved. In the case where the injection port 63 is formed instead of the sub port 62, the compressor 110 can increase the flow rate of the liquid-phase working fluid to be injected, and can lower the discharge temperature more efficiently.

  Further, for example, when a notch is provided in the tip seal as in the related art, gas leakage from the notch to between adjacent compression chambers may occur, and the performance of the compressor may be significantly reduced. Furthermore, the strength of the tip seal may decrease due to stress concentration on the notch of the tip seal. In the compressor 110, the chip seal 83 is disposed at a position away from the sub port 62 or the injection port 63, and the chip seal 83 is not provided with a notch. Therefore, in the compressor 110, gas leakage does not occur between the compression chambers, and the strength of the tip seal 83 does not decrease due to stress concentration.

  Further, in the compressor 110, the tip seal 83 is integrally formed by joining two curved portions of the first curved portion 83a and the second curved portion 83b having the above configuration. The compressor 110 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the conventional case, and arranges the tip seal 80 of the fixed scroll 60 and the orbiting scroll 70 when the tip seal 80 is disposed at the center 71 a of the tip end surface of the fixed spiral wrap portion 61. Of the tip seal 83 is different. Therefore, the compressor 110 can prevent the tip seal 83 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled alternately by mistake.

  Further, since the tip seal 83 of the compressor 110 smoothly connects a plurality of curves to each other, the fitting groove of the tip seal 83 can be processed at a time with a single stroke in the orbiting scroll 70, and excellent processing is achieved. Nature can be secured.

  Further, the compressor 110 can reduce the number of curves constituting the tip seal 83 as compared with the compressor 100 according to the first embodiment. For this reason, when the compressor 110 processes the fitting groove of the tip seal 83 on the tip end surface of the swinging spiral wrap portion 71, the number of boundaries constituting the groove is reduced, and the fitting groove of the tip seal 83 is formed at this boundary. Processing defects such as steps are less likely to occur.

Embodiment 3 FIG.
FIG. 8 is an axial sectional view showing the shapes of the orbiting scroll 70, the fixed scroll 60, and the tip seal 84 in the compressor 120 according to Embodiment 3 of the present invention. Parts having the same configuration as the compressor 100 and the compressor 110 in FIGS. 1 to 7 are denoted by the same reference numerals, and the description thereof will be omitted. The compressor 120 is the same as the compressor 100 except that the configuration of the tip seal 84 differs from the configuration of the tip seal 82 of the compressor 100.

  A tip seal fitting groove 81 having the same shape as the tip seal 84 is formed on the tip end surface of the wrap of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 84 fits into the tip seal fitting groove 81. Have been. The tip seal 84 of the orbiting scroll 70 is disposed at the tip of the orbiting spiral wrap 71 along the spiral direction, and is in contact with the fixed scroll base plate 64 of the fixed scroll 60 facing the same. A tip seal 84 (not shown) of the fixed scroll 60 is disposed at the tip of the fixed scroll wrap 61 along the spiral direction, and is in contact with the swing scroll base plate 74 of the swing scroll 70 facing the spiral scroll wrap 61. The tip seal 84 slides while being pressed against the fixed scroll base plate 64 during the operation of the compressor 120, so that the gap between the swinging spiral wrap 71 and the fixed scroll base plate 64, and the fixed spiral wrap The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 84 slides while being pressed against the oscillating swirl plate 74 during the operation of the compressor 120, so that the gap between the fixed swirl wrap portion 61 and the oscillating swirl plate 74 is fixed. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 or the injection port 63 is provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approaches the tip seal 84 provided on the tip end surface of the oscillating scroll 70. In order to ensure the sealing performance of the tip seal 84, the diameter of the sub port 62 or the injection port 63 needs to be set within a range where the tip seal 84 is not completely straddled.

  In the compressor 120, as shown in FIG. 8, the tip seal 84 is constituted by a plurality of curves having different curvatures, and includes a first curved portion 84a, a second curved portion 84b, and a third curved portion 84c. , A fourth curved portion 84d and a fifth curved portion 84e. As shown in FIG. 8, in the compressor 120, the tip seal 84 includes a first curved portion 84a, a second curved portion 84b, a third curved portion 84c, a fourth curved portion 84d, and a fifth curved portion 84e. Are integrally formed by joining the five curved portions. In FIG. 8, the chip seal 84 is illustrated as having a break in order to clearly indicate the boundary between the curves, but the boundary between the five curves is not divided, and the chip seal 84 is an integral body without a break. is there. That is, in the tip seal 84, a plurality of curves having different curvatures are continuously formed.

  The tip seal 84 has a first curved portion 84a in which the portion approaching the subport 62a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge portion 71b side with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. Having. Alternatively, in the tip seal 84, the portion approaching the injection port 63 a on the outward surface of the fixed scroll 60 passes through the outer peripheral edge 71 b side with respect to the widthwise center 71 a of the orbiting spiral wrap portion 71. It has a curved portion 84a. The first curved portion 84a is formed of, for example, an involute curve having the same curvature as that of the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The tip seal 84 is such that the portion approaching the subport 62b on the inward surface side of the fixed scroll 60 has a second curved portion passing through the inner peripheral edge 71c side with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. 84b. Alternatively, in the tip seal 84, the portion approaching the injection port 63 b on the inward surface side of the fixed scroll 60 passes through the inner peripheral edge 71 c side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has two curved portions 84b. The second curved portion 84b is formed of, for example, an involute curve having the same curvature as that of the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The boundary between the first curved portion 84a and the second curved portion 84b is connected by a third curved portion 84c formed into a smooth curve such as an involute curve having a curvature larger than that of the orbiting scroll 70. The fourth curved portion 84d of the tip seal 84 smoothly connects the ends of the adjacent curved first curved portion 84a and fifth curved portion 84e using an involute curve having a smaller pitch than the orbiting scroll 70. I have. The fifth curved portion 84e of the tip seal 84 is formed as an involute curve passing through the center of the swing spiral wrap portion 71.

  In the compressor 120 according to the third embodiment, the tip seal 84 is constituted by five curved portions, but the number of curved portions constituting the tip seal 84 is changed according to the number of the subports 62 or the injection ports 63. It goes without saying that it is good. Note that the shape of the tip seal 84 of the fixed scroll 60 is formed by an involute curve having the same curvature as that of the fixed spiral wrap portion 61 of the fixed scroll 60, and the center 71a in the width direction of the fixed spiral wrap portion 61 of the fixed scroll 60, as before. May be arranged.

  As described above, the tip seal 84 of the compressor 120 is configured such that the portion approaching the subport 62 or the injection port 63 is located at the outer peripheral edge portion 71b side with respect to the center 71a of the swing spiral wrap portion 71 in the width direction. It is arranged on the inner edge 71c side. That is, the portions of the tip seal 84 approaching the subport 62a on the outward surface of the fixed scroll 60 and the subport 62b on the inward surface of the fixed scroll 60 are away from the subport 62 with respect to the center 71a of the orbiting spiral wrap 71, respectively. Located on the side. Therefore, the compressor 120 can secure the seal width δ larger than the case where the tip seal 84 is formed in one involute shape and is arranged at the center 71 a of the swinging spiral wrap portion 71, and the The diameter can be designed to be large.

  Specifically, when the tip seal 84 is disposed at the center 71a of the tip end surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the subport 62 is set to "(wrap portion) in order to satisfy the seal width δ> 0. Width / 2) + (tip seal width / 2) ”. On the other hand, in the compressor 120, the tip seal 84 has five curved portions 84a, a second curved portion 84b, a third curved portion 84c, a fourth curved portion 84d, and a fifth curved portion 84e. It is integrally formed by connecting curved parts. Therefore, the compressor 120 can enlarge the diameter of the subport 62 beyond this restriction value.

  Further, the injection port 63 of the compressor 120 provided with the injection port 63 instead of the sub port 62 can be similarly designed to be large. In the compressor 120, the injection port 63 a of the tip seal 84 and the portion approaching the injection port 63 b are respectively disposed on the side away from the injection port 63 with respect to the center 71 a of the swing spiral wrap portion 71. Therefore, the compressor 120 can secure the seal width δ larger than the case where the tip seal 84 is formed in one involute shape and is disposed at the center 71 a of the swing spiral wrap portion 71, and the injection port 63 Can be designed with a large diameter.

  Specifically, when the tip seal 84 is disposed at the center 71a of the tip end surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the injection port 63 is set to "(wrap (Part width / 2) + (tip seal width / 2) ”. The compressor 120 is configured such that the tip seal 84 has the first curved portion 84a, the second curved portion 84b, the third curved portion 84c, the fourth curved portion 84d, and the fifth curved portion 84e having the above-described configuration. It is integrally formed by connecting curved parts. Therefore, the compressor 120 can enlarge the diameter of the injection port 63 beyond this restriction value.

  Accordingly, the resistance of the compressor 120 when the working gas is discharged from the subport 62 is reduced, and the performance of the compressor 120 can be improved. Further, when the injection port 63 is formed instead of the sub port 62, the compressor 120 increases the flow rate of the liquid-phase working fluid to be injected, and can more efficiently lower the discharge temperature.

  Further, for example, when a notch is provided in the tip seal as in the related art, gas leakage from the notch to between adjacent compression chambers may occur, and the performance of the compressor may be significantly reduced. Furthermore, the strength of the tip seal may decrease due to stress concentration on the notch of the tip seal. In the compressor 120, the chip seal 84 is arranged at a position away from the sub port 62 or the injection port 63, and the chip seal 84 is not provided with a notch. Therefore, in the compressor 120, gas leakage does not occur between the compression chambers, and the strength of the tip seal 84 does not decrease due to stress concentration.

  In the compressor 120, the tip seal 84 includes the first curved portion 84a, the second curved portion 84b, the third curved portion 84c, the fourth curved portion 84d, and the fifth curved portion 84e having the above configuration. The five curved portions are joined to be integrally formed. The compressor 120 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the related art, and arranges the tip seal 80 of the fixed scroll 60 and the orbiting scroll 70 when it is disposed at the center 71 a of the distal end surface of the fixed spiral wrap portion 61. Are different in the shape of the tip seal 84. Therefore, the compressor 120 can prevent the tip seal 84 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled alternately by mistake.

  In addition, since the tip seal 84 of the compressor 120 smoothly connects a plurality of curves, the fitting groove of the tip seal 84 can be machined at a time with a single stroke in the orbiting scroll 70. Nature can be secured.

  In general, a portion of the tip surface of the spiral wrap where the tip seal is not fitted becomes a leakage flow path between adjacent compression chambers. If the tip seal is displaced from the center of the tip end surface of the wrap, the leakage flow rate between the inside and outside of the tip seal is different, so that a pressure imbalance occurs in the two symmetrical compression chambers. This pressure imbalance generates a force for rotating the spiral, which may affect the reliability of the spiral and the Oldham ring 41. On the other hand, in the tip seal 84, the compressor 120 includes the fourth curved portion 84d and the fifth curved portion 84e located outside the spiral from the first curved portion 84a approaching the subport 62a on the outward surface side of the fixed scroll 60. Are arranged at the center 71 a of the swinging spiral wrap portion 71. Therefore, in the compressor 120, since the width of both sides of the fitting groove of the tip seal 84 formed in the oscillating spiral wrap portion 71 is uniform, the amount of leakage of the symmetrical compression chamber becomes uniform, and the orbiting scroll The movement of 70 is stable, and high reliability is obtained.

Embodiment 4 FIG.
FIG. 9 is an axial cross-sectional view illustrating shapes of orbiting scroll 70, fixed scroll 60, and tip seal 85 in compressor 130 according to Embodiment 4 of the present invention. Parts having the same configurations as those of the compressor 100, the compressor 110, and the compressor 120 in FIGS. 1 to 8 are denoted by the same reference numerals, and description thereof will be omitted. The compressor 130 is the same as the compressor 100 except that the configuration of the tip seal 85 differs from the configuration of the tip seal 82 of the compressor 100.

  A tip seal fitting groove 81 having the same shape as the tip seal 85 is formed on the wrap distal end surface of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 85 is fitted into the tip seal fitting groove 81. Have been. The tip seal 85 of the orbiting scroll 70 is disposed at the tip of the orbiting spiral wrap 71 along the spiral direction, and is in contact with the fixed spiral base plate 64 of the fixed scroll 60 facing the same. In addition, a tip seal 85 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip of the fixed scroll wrap portion 61, and comes into contact with the swinging scroll base plate portion 74 of the swinging scroll 70 facing the same. The tip seal 85 slides while being pressed against the fixed spiral base plate portion 64 during the operation of the compressor 130, so that the gap between the swinging spiral wrap portion 71 and the fixed spiral base plate portion 64, and the fixed spiral wrap portion The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 85 slides while being pressed against the oscillating swirl base plate 74 during operation of the compressor 130, so that the gap between the fixed swirl wrap part 61 and the oscillating swirl base plate 74 and the fixed state. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 or the injection port 63 is provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approaches the tip seal 85 provided on the tip end surface of the oscillating scroll 70. In order to ensure the sealing performance of the tip seal 85, the diameter of the sub port 62 or the injection port 63 needs to be set within a range where the tip seal 85 is not completely straddled.

  As shown in FIG. 9, the tip seal 85 is constituted by a plurality of curves having different curvatures, and is constituted by having two curved portions of a first curved portion 85a and a second curved portion 85b. ing. In the tip seal 85, the portion approaching the sub port 62 or the injection port 63 is located on the outer peripheral edge 71 b side and the inner peripheral edge 71 c side with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. Are located. The tip seal 85 has a structure in which a first curved portion 85a and a second curved portion 85b are divided. That is, the tip seal 85 is divided into a plurality of curves having different curvatures. In the tip seal 85, the first curved portion 85a and the second curved portion 85b may overlap in the spiral curve direction, or may be disposed with a slight gap.

  The tip seal 85 is configured such that a portion approaching the subport 62 a on the outward surface side of the fixed scroll 60 has a first curved portion 85 a passing through the outer peripheral edge 71 b side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. Having. Alternatively, in the tip seal 85, the portion approaching the injection port 63 a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71 b side with respect to the widthwise center 71 a of the orbiting spiral wrap portion 71. It has a curved portion 85a. The first curved portion 85a is formed by an involute curve having the same curvature as that of the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  The tip seal 85 is configured such that a portion approaching the subport 62 b on the inward surface side of the fixed scroll 60 is a second curved portion that passes through the inner peripheral edge 71 c side with respect to the widthwise center 71 a of the orbiting spiral wrap portion 71. 85b. Alternatively, in the tip seal 85, the portion approaching the injection port 63 b on the inward surface side of the fixed scroll 60 passes through the inner peripheral edge 71 c side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has two curved portions 85b. The second curved portion 85b is configured by an involute curve having the same curvature as that of the orbiting spiral wrap portion 71 of the orbiting scroll 70.

  In the compressor 130 according to the fourth embodiment, the tip seal 85 is constituted by two curved portions, but the number of curved portions constituting the tip seal 85 is changed according to the number of the subports 62 or the injection ports 63. It goes without saying that it is good. Note that the shape of the tip seal 85 of the fixed scroll 60 is formed by an involute curve having the same curvature as that of the fixed spiral wrap portion 61 of the fixed scroll 60, and the center 71a in the width direction of the fixed spiral wrap portion 61 of the fixed scroll 60 as in the related art. May be arranged.

  As described above, the tip seal 85 of the compressor 130 is configured such that the portion approaching the sub port 62 or the injection port 63 has the outer peripheral edge portion 71b side and the center 71a in the width direction of the swing spiral wrap portion 71. It is arranged on the inner edge 71c side. That is, the portions of the tip seal 85 approaching the subport 62a on the outward surface of the fixed scroll 60 and the subport 62b on the inward surface of the fixed scroll 60 are away from the subport 62 with respect to the center 71a of the orbiting spiral wrap 71, respectively. Located on the side. Therefore, the compressor 130 can secure the seal width δ larger than the case where the tip seal 85 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the The diameter can be designed to be large.

  Specifically, when the tip seal 85 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the subport 62 is set to “(wrap portion) in order to satisfy the seal width δ> 0. Width / 2) + (tip seal width / 2) ”. On the other hand, in the compressor 130, the tip seal 85 is configured to have two curved portions of the first curved portion 85a and the second curved portion 85b. Therefore, the compressor 130 can increase the diameter of the subport 62 beyond this restriction value.

  Further, the injection port 63 of the compressor 130 having the injection port 63 in place of the sub port 62 can be similarly designed to be large. In the compressor 130, the injection port 63 a of the tip seal 85 and the portion approaching the injection port 63 b are respectively located on the side away from the injection port 63 with respect to the center 71 a of the swing spiral wrap portion 71. Therefore, the compressor 130 can secure the seal width δ larger than the case where the tip seal 85 is formed in one involute shape and is arranged at the center 71 a of the oscillating spiral wrap portion 71, and the injection port 63 Can be designed with a large diameter.

  Specifically, when the tip seal 85 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, in order to satisfy the seal width δ> 0, the diameter of the injection port 63 is set to “(wrap (Part width / 2) + (tip seal width / 2) ”. The compressor 130 is configured such that the tip seal 85 has two curved portions of the first curved portion 85a and the second curved portion 85b having the above configuration. Therefore, the compressor 130 can enlarge the diameter of the injection port 63 beyond this restriction value.

  Accordingly, the resistance of the compressor 130 when the working gas is discharged from the subport 62 is reduced, and the performance can be improved. In the case where the injection port 63 is formed instead of the sub port 62, the compressor 130 increases the flow rate of the liquid-phase working fluid to be injected, and can lower the discharge temperature more efficiently.

  Further, for example, when a notch is provided in the tip seal as in the related art, gas leakage from the notch to between adjacent compression chambers may occur, and the performance of the compressor may be significantly reduced. Furthermore, the strength of the tip seal may decrease due to stress concentration on the notch of the tip seal. In the compressor 130, the chip seal 85 is disposed at a position away from the sub port 62 or the injection port 63, and the chip seal 85 is not provided with a notch. Therefore, in the compressor 130, gas leakage does not occur between the compression chambers, and the strength of the tip seal 85 does not decrease due to stress concentration.

  Further, in the compressor 130, the tip seal 85 is configured to have two curved portions of the first curved portion 85a and the second curved portion 85b having the above configuration. The compressor 130 forms the tip seal 80 of the fixed scroll 60 with an involute curve in the same manner as the conventional case, and arranges the tip seal 80 of the fixed scroll 60 and the orbiting scroll 70 when the tip seal 80 is disposed at the center 71 a of the tip end surface of the fixed spiral wrap portion 61. Of the tip seal 85 is different. Therefore, the compressor 130 can prevent the tip seal 85 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled alternately by mistake.

  According to the compressor 130 according to the fourth embodiment, since there is no seam of a different curve in the fitting groove of the tip seal 85 provided in the oscillating spiral wrap portion 71, processing is easy. Therefore, the compressor 130 does not cause a manufacturing defect such as a step occurring at the boundary of the curve of the fitting groove of the tip seal 85. Further, the compressor 130 can easily produce a die for the tip seal 85.

Embodiment 5 FIG.
FIG. 10 is an axial sectional view showing shapes of orbiting scroll 70, fixed scroll 60, and tip seal 86 in compressor 140 according to Embodiment 5 of the present invention. Parts having the same configurations as those of the compressor 100, the compressor 110, the compressor 120, and the compressor 130 in FIGS. 1 to 9 are denoted by the same reference numerals, and description thereof will be omitted. The compressor 140 is the same as the compressor 100 except that the configuration of the tip seal 86 is different from the configuration of the tip seal 82 of the compressor 100.

  A tip seal fitting groove 81 having the same shape as the tip seal 86 is formed on the tip end surface of the wrap of the fixed scroll 60 and the orbiting scroll 70, and the tip seal 86 fits into the tip seal fitting groove 81. Have been. The tip seal 86 of the orbiting scroll 70 is disposed at the tip of the orbiting spiral wrap 71 along the spiral direction, and is in contact with the fixed spiral base plate portion 64 of the fixed scroll 60 facing the same. Further, a tip seal 86 (not shown) of the fixed scroll 60 is disposed at the tip of the fixed scroll wrap portion 61 along the spiral direction, and is in contact with the swinging scroll base plate portion 74 of the swing scroll 70 facing the same. The tip seal 86 slides while being pressed against the fixed spiral base plate portion 64 during operation of the compressor 140, thereby forming a gap between the swing spiral wrap portion 71 and the fixed spiral base plate portion 64, and a fixed spiral wrap portion. The gap between the swirling spiral wrap portion 61 and the swirling spiral wrap portion 71 is filled to prevent leakage of the working gas. Alternatively, the tip seal 86 slides while being pressed against the oscillating swirl plate 74 during the operation of the compressor 140, so that the gap between the fixed swirl wrap portion 61 and the oscillating swirl plate 74 is fixed. The gap between the spiral wrap 61 and the swinging spiral wrap 71 is filled to prevent leakage of the working gas. The sub port 62 or the injection port 63 is provided on the fixed scroll base plate portion 64 of the fixed scroll 60, and approaches the tip seal 86 provided on the wrap tip surface of the orbiting scroll 70. In order to ensure the sealing performance of the tip seal 86, the diameter of the sub port 62 or the injection port 63 needs to be set within a range that does not completely straddle the tip seal 86.

  In the compressor 140, the tip seal 86 of the orbiting scroll 70 has a plurality of curves having different curvatures, and has an involute portion 86a and an R portion 86b. In the tip seal 86, a plurality of curves having different curvatures are continuously formed. The R portion 86b of the tip seal 86 is disposed at a position approaching the subport 62 or the injection port 63, and is formed in a curved arc shape so as to avoid the subport 62 or the injection port 63. The tip seal 86 has a portion other than the R portion 86b constituted by an involute portion 86a. The involute portion 86a is disposed on the wrap tip surface of the orbiting scroll 70, and is formed as an involute curve having the same curvature as the orbiting spiral wrap portion 71 through the center 71a in the width direction of the orbiting spiral wrap portion 71. The width of the R portion 86b is the same as the width of the involute portion 86a, but may be different.

  The tip seal 86 has an R portion 86b1 in which the portion approaching the subport 62a on the outward surface side of the fixed scroll 60 passes through the outer peripheral edge 71b side with respect to the center 71a in the width direction of the orbiting spiral wrap portion 71. . Alternatively, in the tip seal 86, the portion approaching the injection port 63 a on the outward surface side of the fixed scroll 60 has an R portion that passes through the outer peripheral edge 71 b side with respect to the widthwise center 71 a of the orbiting spiral wrap portion 71. 86b1.

  In the tip seal 86, the portion approaching the subport 62 b on the inward surface side of the fixed scroll 60 passes through the R portion 86 b 2 passing through the inner peripheral edge 71 c side with respect to the widthwise center 71 a of the oscillating spiral wrap portion 71. Have. Alternatively, in the tip seal 86, the portion approaching the injection port 63 b on the inward surface side of the fixed scroll 60 passes through the inner edge 71 c side with respect to the center 71 a in the width direction of the orbiting spiral wrap portion 71. It has a portion 86b2.

  In the compressor 140 according to the fifth embodiment, the tip seal 86 has two R portions 86b, but the number of the R portions 86b constituting the tip seal 86 depends on the number of the subports 62 or the injection ports 63. Needless to say, it is better to change. Note that the shape of the tip seal 86 of the fixed scroll 60 is formed by an involute curve having the same curvature as the fixed spiral wrap portion 61 of the fixed scroll 60, and the center 71a in the width direction of the fixed spiral wrap portion 61 of the fixed scroll 60 as in the related art. May be arranged.

  As described above, in the tip seal 86 of the compressor 140, the portion approaching the sub-port 62 or the injection port 63 is located at the outer peripheral edge portion 71b side with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It is arranged on the inner edge 71c side. That is, the portions of the tip seal 86 approaching the subport 62a on the outward surface of the fixed scroll 60 and the subport 62b on the inward surface of the fixed scroll 60 are separated from the subport 62 with respect to the center 71a of the orbiting spiral wrap 71, respectively. Located on the side. Therefore, the compressor 140 can secure the seal width δ larger than the case where the tip seal 86 is formed in one involute shape and is arranged at the center 71 a of the swing spiral wrap portion 71, and the The diameter can be designed to be large.

  Specifically, when the tip seal 86 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the subport 62 is set to “(wrap portion) in order to satisfy the seal width δ> 0. Width / 2) + (tip seal width / 2) ”. On the other hand, the compressor 140 is configured such that the tip seal 86 has an R portion 86b curved and formed in an arc shape so as to avoid the sub port 62 or the injection port 63, and an involute portion 86a. . Therefore, the compressor 140 can increase the diameter of the subport 62 beyond this restriction value.

  Further, the injection port 63 of the compressor 140 provided with the injection port 63 instead of the subport 62 can be similarly designed to be large. In the compressor 140, the injection port 63 a of the tip seal 86 and the portion approaching the injection port 63 b are respectively disposed on the side away from the injection port 63 with respect to the center 71 a of the swing spiral wrap portion 71. Therefore, the compressor 140 can secure the seal width δ larger than the case where the tip seal 86 is formed in one involute shape and is disposed at the center 71 a of the swing spiral wrap portion 71, and the injection port 63 Can be designed with a large diameter.

  Specifically, when the tip seal 86 is disposed at the center 71a of the tip surface of the swinging spiral wrap portion 71 as in the related art, the diameter of the injection port 63 is set to "(wrap) in order to satisfy the seal width δ> 0. (Part width / 2) + (tip seal width / 2) ”. In the compressor 140, the tip seal 86 includes an R portion 86b formed in a curved arc shape so as to avoid the subport 62 or the injection port 63, and an involute portion 86a. Therefore, the compressor 140 can enlarge the diameter of the injection port 63 beyond this restriction value.

  Thus, the resistance of the compressor 140 when the working gas is discharged from the subport 62 is reduced, and the performance of the compressor 140 can be improved. Further, when the injection port 63 is formed instead of the sub port 62, the compressor 140 can increase the flow rate of the liquid-phase working fluid to be injected, and can lower the discharge temperature more efficiently.

  Further, for example, when a notch is provided in the tip seal as in the related art, gas leakage from the notch to between adjacent compression chambers may occur, and the performance of the compressor may be significantly reduced. Furthermore, the strength of the tip seal may decrease due to stress concentration on the notch of the tip seal. In the compressor 140, the chip seal 86 is disposed at a position away from the sub port 62 or the injection port 63, and the chip seal 86 is not provided with a notch. Therefore, in the compressor 140, gas leakage does not occur between the compression chambers, and the strength of the tip seal 86 does not decrease due to stress concentration.

  Further, the compressor 140 is configured such that the tip seal 86 has an R portion 86b formed in a curved arc shape so as to avoid the subport 62 or the injection port 63, and an involute portion 86a. The compressor 140 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the related art, and when the tip seal 80 is disposed at the center 71 a of the tip end surface of the fixed spiral wrap portion 61, the tip seal 80 of the fixed scroll 60 and the orbiting scroll 70 Of the tip seal 86 is different. Therefore, the compressor 140 can prevent the tip seal 86 of the orbiting scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled alternately by mistake.

  The compressor 140 has an R portion 86b that is curved and formed in an arc shape so as to avoid the sub port 62 or the injection port 63. Therefore, the compressor 140 can dispose the tip seal 86 away from the sub port 62 or the injection port 63 only in a minimum range approaching the sub port 62 or the injection port 63. In the compressor 140, the involute portion 86a is disposed at the center 71a of the tip end surface of the swing spiral wrap portion 71 except for the R portion 86b. Therefore, the compressor 140 can achieve high reliability because the imbalance of the amount of leakage between the inside and the outside of the tip seal 86 is minimized, and the imbalance of the pressure in the compression chambers at the symmetric positions is also small. Can be

  The present invention is not limited to the above embodiment, and various modifications are possible. For example, in the above embodiment, the case where the compressor 100 is a low-pressure shell type is illustrated, but the compressor 100 may be a high-pressure shell type.

  Reference Signs List 20 shell, 20a lower shell, 20b center shell, 20c upper shell, 21 oil sump, 23 oil pump, 24 oil drain pipe, 25 frame, 25a suction port, 26 subframe, 27 suction pipe, 28 discharge pipe, 29 muffler, 30 Motor, 31 rotor, 32 stator, 40 compression section, 40a compression chamber, 40b compression chamber, 41 Oldham ring, 41a Oldham groove, 42 slider, 43 swing bearing, 44 sleeve, 45 low pressure chamber, 46 high pressure chamber, 50 shaft , 50a oil supply path, 52 first balancer, 52a balancer cover, 53 second balancer, 54 main bearing, 55 sub bearing, 60 fixed scroll, 61 fixed spiral wrap, 62 subport, 62a subport, 62b subport, 63 injection port 63a injection port, 63b injection port, 64 fixed swirl base plate, 65 discharge port, 70 swing scroll, 71 swing swirl wrap, 71a center, 71b edge, 71c edge, 74 swing swirl plate Part, 80 chip seal, 81 groove for chip seal fitting, 82 chip seal, 82a first curved part, 82b second curved part, 82c third curved part, 83 chip seal, 83a first curved part, 83b second curved part , 84 chip seal, 84a first curved part, 84b second curved part, 84c third curved part, 84d fourth curved part, 84e fifth curved part, 85 chip seal, 85a first curved part, 85b second curved part , 86 chip seal, 86a involute part, 86b R part, 86b1 R part, 86b2 R part, 100 pressure Compressors, 110 compressors, 120 compressors, 130 compressors, 140 compressors.

Claims (14)

A fixed scroll having a base plate portion and a spiral wrap portion formed on the base plate portion,
An orbiting scroll including a base plate portion and a spiral wrap portion formed on the base plate portion,
Has,
The fixed scroll has at least one subport for discharging a working gas or at least one injection port for injecting a liquid-phase working fluid,
The orbiting scroll,
A tip seal is provided along the spiral direction at the tip of the spiral wrap portion, and is in contact with the base plate portion of the fixed scroll facing,
The compressor in which the tip seal is provided such that a portion approaching the subport or the injection port is located on an edge side with respect to a center in a width direction of the spiral wrap portion.   The compressor according to claim 1, wherein the tip seal is configured by a plurality of curves having different curvatures.   The compressor according to claim 2, wherein the tip seal has a plurality of curves having different curvatures formed continuously.   The compressor according to claim 2, wherein the tip seal is divided for each of a plurality of curves having different curvatures. The tip seal,
The part which approaches the said subport or the said injection port has the 1st curve part which passes the outer peripheral edge part side with respect to the center of the width direction of the said spiral wrap part, The Claims any one of Claims 1-4. Compressor.   The compressor according to claim 5, wherein the first curved portion is formed by an involute curve having the same curvature as the spiral wrap portion. The tip seal,
The part which approaches the said subport or the said injection port has the 2nd curved part which passes the edge part side of an inner periphery with respect to the center of the width direction of the said spiral wrap part in any one of Claims 1-6. The compressor as described.   The compressor according to claim 7, wherein the second curved portion is formed by an involute curve having the same curvature as the spiral wrap portion.   The compressor according to claim 7, wherein the second curved portion is formed by an involute curve having a larger curvature than the spiral wrap portion. The tip seal,
The compressor according to any one of claims 5 to 9, further comprising a third curved portion formed by an involute curve having a larger curvature than the spiral wrap portion. The tip seal,
The compressor according to claim 10, further comprising a fourth curved portion formed by an involute curve having a smaller curvature than the spiral wrap portion. The tip seal,
The compressor according to claim 11, further comprising a fifth curved portion passing through the center in the width direction of the spiral wrap portion. The tip seal,
The portion approaching the subport or the injection port is formed by an R portion curved and formed in an arc shape, and an involute curve having the same curvature as the spiral wrap portion passing through the center in the width direction of the spiral wrap portion. The compressor according to any one of claims 1 to 4, further comprising an involute section. The fixed scroll,
A tip seal is provided along the spiral direction at the tip of the spiral wrap portion, and is in contact with the base plate portion of the orbiting scroll that faces,
The tip seal of the fixed scroll is formed by an involute curve having the same curvature as the spiral wrap portion of the fixed scroll, and is disposed at the center in the width direction of the spiral wrap portion of the fixed scroll. A compressor according to any one of the preceding claims.

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