WO2019043741A1

WO2019043741A1 - Compressor

Info

Publication number: WO2019043741A1
Application number: PCT/JP2017/030659
Authority: WO
Inventors: 祐司 ▲高▼村; 友寿松井; 浩平達脇
Original assignee: 三菱電機株式会社
Priority date: 2017-08-28
Filing date: 2017-08-28
Publication date: 2019-03-07
Also published as: JP6861829B2; JPWO2019043741A1

Abstract

This compressor has: a stationary scroll provided with a base plate and a spiral wrap which is formed on the base plate; and an orbiting scroll provided with a base plate and a spiral wrap which is formed on the base plate. The stationary scroll has formed therein at least one sub-port for discharging an operating gas, or at least one injection port for injecting a liquid-phase operating fluid. The orbiting scroll is provided with a tip seal disposed at the tip of the spiral wrap in the spiral direction and in contact with the base plate of the stationary scroll, toward which the tip seal faces. The portion of the tip seal, which moves toward the sub-port or the injection port, is disposed offset to the edge side with respect to the center of the spiral wrap in the width direction thereof.

Description

Compressor

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

Conventionally, a scroll compressor is known as one of compressors used for a refrigerator, an air conditioner, and the like. The scroll compressor has a fixed scroll and a rocking scroll, and the rocking scroll performs a revolving orbiting motion with respect to the fixed scroll. The fixed scroll and the oscillating scroll are members in which spiral wraps are formed on surfaces facing each other, and a compression chamber is formed by the combined wraps. And a scroll compressor changes the internal volume of a compression chamber by rocking | fluctuation scroll rock | fluctuating, and compresses the working gas which flowed in into the compression chamber. A seal member called a tip seal is fitted to the tip end surface of the spiral wrap portion in the fixed scroll and the swing scroll. The tip seal is lifted by back pressure during operation of the compressor, and the working gas leaks between adjacent compression chambers by filling the gap between the tip end face of the lap portion and the base plate face of the opposing scroll. Play the function to prevent.

Patent Document 1 discloses a scroll compressor in which a notch is provided in a portion where a tip seal interferes with a subport, thereby preventing interference between the tip seal and the subport and preventing wear of the tip seal due to catching on the subport. .

Japanese Utility Model Publication No. 61-41882

The subport formed in the fixed scroll has a function of preventing the occurrence of power loss due to overcompression by discharging the working gas from the middle of the scroll during operation under the low compression ratio condition. In the compressor, the larger the diameter of the subport, the smaller the flow path resistance, and the reduction effect of the power loss due to over-compression can be obtained. However, since the subport is provided at a position approaching the tip seal provided on the oscillating scroll, the diameter of the subport is excessively increased, and if the subport straddles the tip seal, the adjacent compression chambers are adjacent to each other through the subport. It will cause a leak of 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 Document 1 does not have the effect of expanding the seal width by the tip seal, and the diameter of the subport or the diameter of the injection port can be expressed by (lap width / 2 + tip seal width / 2). Can not be too big. Therefore, the subport can not secure a sufficient flow passage area, and the compressor may generate an overcompression loss. Further, the injection port can not secure a sufficient flow passage area, and the discharge temperature of the compressor may increase due to the shortage of the injection flow rate.

The present invention has been made against the background described above, and an object of the present invention is to provide a compressor which secures a large diameter of a sub port or a diameter of an injection port even when a chip seal is used.

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

According to the present invention, the tip seal is arranged such that the portion approaching the sub port or the injection port is located on the end edge side with respect to the widthwise center of the spiral wrap. That is, the tip seal is disposed on the side away from the sub port or the injection port with respect to the center of the swing scroll wrap. Therefore, the compressor can secure a larger seal width by the tip seal than the case where the tip seal is formed in one involute shape and disposed at the center of the swing lap portion, and the diameter of the sub port or injection port Can be designed large.

It is an axial sectional view showing the compressor concerning Embodiment 1 of the present invention. FIG. 1 is a horizontal cross-sectional view showing the shapes of a rocking scroll, a stationary scroll and a tip seal in the prior art. It is an enlarged view which shows the rocking scroll and fixed scroll which the rocking scroll of FIG. 2 moved. It is a perpendicular direction sectional view which shows the relationship between the tip seal of FIG. 3, and a subport or an injection port. It is a perpendicular direction sectional view of a compression part when a tip seal does not contact with a fixed scroll. It is an axial sectional view showing the shape of a rocking scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 1 of the present invention. It is an axial sectional view showing the shape of a rocking scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 2 of the present invention. It is an axial sectional view showing the shape of a rocking scroll, a fixed scroll, and a tip seal in a compressor according to Embodiment 3 of the present invention. It is an axial sectional view showing the shape of a rocking scroll, a fixed scroll and a tip seal in a compressor according to a fourth embodiment of the present invention. It is an axial sectional view showing the shape of a rocking 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 respective constituent members may differ from the actual ones. Moreover, in the following drawings, what attached | subjected the same code | symbol is the same or it corresponds to this, and this shall be common in the whole text of a specification. In addition, terms that indicate direction (for example, "upper", "lower", "right", "left", "front", "rear", etc.) are appropriately used to facilitate understanding, but their notation is For the convenience of the description, it is only described as such, and does not limit the arrangement and orientation of the device or parts.

Embodiment 1
[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 high temperature and high pressure state. As shown in FIG. 1, the compressor 100 includes a shell 20, a motor 30, a compression unit 40, and a shaft unit 50. The compressor 100 is a low pressure shell compressor.

[Shell 20]
The shell 20 constitutes 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 cylindrical, and an upper shell 20c closing the top of the central shell 20b. Have. The shell 20 has an oil sump 21 at its bottom for storing oil. At a lower portion of the shell 20, an oil pump 23 disposed in an oil reservoir 21 of the shell 20 is accommodated. The oil pump 23 is attached to one end side of the shaft portion 50, sucks the oil stored in the oil reservoir 21 of the shell 20, and supplies the oil to the oil supply passage 50a in the shaft portion 50. The oil supplied to the oil supply passage 50 a is supplied to the bearing portion inside the compressor 100 and the Oldham ring 41. The oil lubricates and cools the bearing portion and the Oldham ring 41. A suction pipe 27 is provided on the side of the shell 20. The suction pipe 27 is a pipe that sucks the working gas into the interior of the shell 20. A discharge pipe 28 is provided at the top of 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 the 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 rocking scroll 70 and the fixed scroll 60 are mounted on the frame 25 in a state in which the spiral wraps are engaged with each other. In the first embodiment, an example in which the fixed scroll 60 is fixed to the frame 25 will be described, but the fixed scroll 60 can 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 the main bearing 54. A suction port 25 a is formed in the frame 25, and the working gas flows into the compression unit 40 through the suction port 25 a. 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 the sub bearing 55.

The oil discharge pipe 24 is a pipe that connects the space between the frame 25 and the oscillating scroll 70 and the space between the frame 25 and the sub-frame 26. The oil discharge pipe 24 causes excess oil out of the oil flowing in the space between the frame 25 and the oscillating 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 its own rotation. The stator 32 is fixed to the shell 20 by shrink fitting or the like. The stator 32 generates a magnetic field by the power supplied from the inverter (not shown) and rotates the rotor 31.

[Compressing unit 40]
The compression unit 40 is provided inside the shell 20 and is driven by the motor 30 to compress the working gas. The compression unit 40 is accommodated in the frame 25 and has a fixed scroll 60 and a swing scroll 70. The fixed scroll 60 is fixed inside the shell 20, and the fixed scroll 60 is provided with a discharge port 65 and a subport 62 for discharging the compressed working gas. The rocking scroll 70 revolves around the fixed scroll 60, and its rotation movement is restricted by the Oldham ring 41. The fixed scroll 60 and the rocking scroll 70 are provided with a spiral fixed spiral wrap portion 61 and a rocking spiral wrap portion 71, which will be described later, on the surfaces facing each other. The compression unit 40 forms a compression chamber in a space in which the fixed spiral wrap unit 61 and the swing spiral wrap unit 71 are engaged. In the compression section 40, when the swing scroll 70 is swung by the rotation of the shaft section 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 rocking scroll 70 and regulates the rotational movement of the rocking scroll 70. The Oldham ring 41 is attached to an Oldham groove 41 a formed on the thrust lower surface of the oscillating scroll 70. The slider 42 is a cylindrical member attached to the outer peripheral surface of the upper portion of the shaft portion 50, and is located on the inner surface of the lower portion of the oscillating scroll 70. That is, the rocking scroll 70 is attached to the shaft portion 50 via the slider 42, and the rocking scroll 70 also rotates with the rotation of the shaft portion 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 the relative inclination of the main bearing 54 and the shaft portion 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 is a bearing structure formed of a slide bearing such as a copper lead alloy, for example, and rotatably supports the shaft 50. In addition, although illustrated about the case where the main bearing 54 consists of slide bearings, you may pivotally support the axial part 50 by another well-known bearing structure. The shaft portion 50 has an oil supply passage 50 a formed therein, and connects the motor 30 and the compression portion 40 to transmit 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 unbalance generated by the oscillating scroll 70 and the slider 42. The first balancer 52 is accommodated in the 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 attached to the lower surface of the rotor 31. The second balancer 53 cancels the unbalance generated by the oscillating scroll 70 and the slider 42.

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

Discharge of the compressed gas from the subport 62 is performed under operating conditions where the compression ratio is small. Since the compressed gas passes through the subport 62 and is bypassed into the upper shell 20c before reaching the center of the compression chamber, the compressor 100 can reduce the power loss due to excessive compression.

The injection port 63 is used to inject a working fluid in a liquid phase into the compression chamber during operation at a high compression ratio condition. The injection port 63 has a function of reducing the temperature of the discharge gas and preventing damage to the fixed scroll 60 and the oscillating scroll 70 due to thermal expansion.

FIG. 2 is a horizontal sectional view showing the shapes of the oscillating scroll 70, the fixed scroll 60 and the tip seal 80 in the prior art. FIG. 3 is an enlarged view showing the swing scroll 70 and the fixed scroll 60 on which the swing scroll 70 of FIG. 2 has moved. The positions of these horizontal cross sections correspond to the line AA in the compressor 100 of FIG. In the following drawings, the positions of the discharge port 65, the sub port 62, and the injection port 63 formed in the fixed scroll base plate portion 64 are also shown in a plan view of the compressor. Also, the generic name of the subport 62a and the subport 62b described below is the subport 62, and the generic name of the injection port 63a and the injection port 63b is 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 using FIGS. 2 and 3. As shown in FIGS. 2 and 3, in the fixed scroll bed portion 64 of the fixed scroll 60, a subport 62 a is formed in the compression chamber 40 a on the outward surface side of the fixed scroll 60, and compression on the inward surface side of the fixed scroll 60 is performed. The subport 62b is formed in the chamber 40b. The sub port 62a and the sub port 62b are disposed at a position where the compression chamber 40a on the fixed scroll outward surface side and the compression chamber 40b on the fixed scroll inward surface side are paired. When the fixed scroll 60 is formed with the injection port 63 instead of the sub port 62, the injection port 63 is formed instead of the sub port 62 of FIGS. In this case, an injection port 63a is formed in the compression chamber 40a on the outward surface side of the fixed scroll 60 in the fixed scroll bed plate portion 64 of the fixed scroll 60, and an injection port 63b is formed in the compression chamber 40b on the inward surface side of the fixed scroll 60. Is formed. The injection port 63a and the injection port 63b are disposed at a position where the compression chamber 40a on the fixed scroll outward surface side and the compression chamber 40b on the fixed scroll inward surface side are paired. The sub port 62 may be one, or a plurality of paired sub ports 62 may be provided. Similarly, one injection port 63 may be provided, and a plurality of injection ports 63 serving as a pair 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 wrap tip end face of the fixed scroll 60 and the oscillating scroll 70, and the tip seal 80 is fitted in the tip seal fitting groove 81. It is done. The tip seal 80 of the rocking scroll 70 is disposed at the tip of the rocking scroll wrap 71 along the spiral direction, and contacts the fixed scroll base plate 64 of the fixed scroll 60 facing it. Further, a tip seal 80 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip of the fixed spiral wrap portion 61, and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing it. The tip seal 80 slides while being pressed against the stationary scroll base plate portion 64 during operation of the compressor 100, so that the gap between the oscillating scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 80 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 100 is in operation, so that the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 is fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 80, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 80 is not completely crossed.

Here, dimensional limitations in the case of 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 with the tip seal 80 of the oscillating scroll 70, the sub port 62 or the injection port 63 needs to be completely sized so that the tip seal 80 of the oscillating scroll 70 is not straddled. There is. In FIG. 3, δ is the contact area between the tip seal 80 and the fixed scroll 60, and is the 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 in FIG. FIG. 5 is a vertical cross-sectional view of the compression unit 40 when the tip seal 80 does not contact the fixed scroll 60. FIG. 4 is a vertical direction 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 to be seal width δ> 0. At this time, the compression section 40 has a seal width δ at which the tip seal 80 of the oscillating scroll 70 and the fixed scroll bed plate section 64 come into contact, so that no leak from the high pressure chamber 46 to the low pressure chamber 45 occurs. The upper limit of the seal width δ is the width γ of the tip seal 80. FIG. 5 is a vertical direction sectional view of the compression section 40 when the seal width δ by the tip seal 80 and the fixed scroll 60 is formed to be seal width δ <0. At this time, since there is no seal width δ at which the tip seal 80 of the swing scroll 70 contacts the fixed scroll table portion 64, the high pressure chamber 46 and the low pressure chamber 45 communicate with each other through the subport 62. The working gas leaks to the low pressure chamber 45. Therefore, the diameter of the sub port 62 or the injection port 63 can be increased only in the range satisfying δ> 0, and in order to provide the diameter of the sub port 62 or the injection port 63 large, the tip seal 80 of the oscillating scroll 70 is used. It is necessary to devise the shape.

FIG. 6 is an axial sectional view showing the 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 end face of the fixed scroll 60 and the oscillating scroll 70, and the tip seal 82 is fitted in the tip seal fitting groove 81. It is done. The tip seal 82 of the oscillating scroll 70 is disposed along the spiral direction at the tip of the oscillating scroll wrap 71 and contacts the fixed scroll base plate 64 of the facing fixed scroll 60. Further, a tip seal 82 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip of the fixed spiral wrap portion 61, and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing it. The tip seal 82 slides while being pressed against the stationary scroll base plate portion 64 while the compressor 100 is in operation, so that the gap between the oscillating scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 82 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 100 is in operation, so that the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 is fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 a tip seal 82 provided on the wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 82, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 82 is not completely crossed.

As shown in FIG. 6, the tip seal 82 is composed of a plurality of curves having different curvatures, and three curves of a first curve portion 82a, a second curve portion 82b, and a third curve portion 82c. The parts are joined together and configured integrally. Although the tip seal 82 is illustrated as having a cut in order to clearly show the boundary of the curve in FIG. 6, the tip seal 82 is a one-piece without break. That is, in the tip seal 82, a plurality of curves having different curvatures are continuously formed. With respect to the tip seal 82, the portion approaching the sub port 62 or the injection port 63 is on the side of the end edge 71b of the outer periphery and the side of the end edge 71c of the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap 71 It is arranged.

The tip seal 82 is a first curved portion 82 a where the portion approaching the subport 62 a on the outward surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. Have. Alternatively, the tip seal 82 may be configured such that a portion approaching the injection port 63 a on the outward facing surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It has a curved portion 82a. The first curve portion 82 a is formed of an involute curve having the same curvature as the swing spiral wrap portion 71 of the swing scroll 70.

The tip seal 82 is a second curved portion in which the portion approaching the subport 62b on the inward facing surface side of the fixed scroll 60 passes the side of the end edge 71c on the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It has 82b. Alternatively, in the tip seal 82, the portion approaching the injection port 63b on the inward surface side of the fixed scroll 60 passes the side of the end edge 71c on the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It has 2 curve part 82b. The second curve portion 82 b is formed of an involute curve having the same curvature as the swing spiral wrap portion 71 of the swing scroll 70.

The boundary between the first curve portion 82a and the second curve portion 82b is joined together by a third curve portion 82c formed into a smooth curve, such as an involute curve having a curvature larger than that of the swing scroll 70, for example. In the compressor 100 according to the first embodiment, the tip seal 82 is formed of three curve portions, but the number of curve portions constituting the tip seal 82 is changed according to the number of sub ports 62 or injection ports 63. Needless to say, it is good. The shape of the tip seal 82 of the fixed scroll 60 is formed by an involute curve having the same curvature as that of the fixed scroll wrap 61 of the fixed scroll 60 as in the prior art, and the center 71 a in the width direction of the fixed scroll wrap 61 of the fixed scroll 60 It may be arranged in

As described above, in the tip seal 82 of the compressor 100, the portion approaching the sub port 62 or the injection port 63 is the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap 71 It is arrange | positioned at the edge part 71c side of inner periphery. That is, the portions of the tip seal 82 approaching the subport 62a on the outward facing surface side of the fixed scroll 60 and the subport 62b on the inward facing surface side of the fixed scroll 60 separate from the subport 62 with respect to the center 71a of the oscillating scroll wrap portion 71. It is arranged on the side. Therefore, the compressor 100 can secure a larger seal width δ as compared with the case where the tip seal 82 is configured in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the sub port 62 The diameter can be designed large.

Specifically, when the tip seal 82 is disposed at the center 71 a of the tip end face of the swing scroll wrap portion 71 as in the prior art, the diameter of the subport 62 is set to “(wrap portion to satisfy seal width δ> 0 The constraint value must be equal to or less than width / 2) + (tip seal width / 2). On the other hand, in the compressor 100, the tip seal 82 is integrally formed by connecting three curve portions of a first curve portion 82a, a second curve portion 82b, and a third curve portion 82c. Therefore, it is possible to enlarge the diameter of the sub port 62 beyond this restriction value.

Further, the injection port 63 can be designed to be large similarly for the compressor 100 in which the injection port 63 is provided instead of the sub port 62. In the compressor 100, the injection port 63a of the tip seal 82 and the portions approaching the injection port 63b are disposed on the side away from the injection port 63 with respect to the center 71a of the oscillating swirl wrap portion 71, respectively. Therefore, the compressor 100 can secure a large seal width δ as compared with the case where the tip seal 82 is configured in a single involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the injection port 63. The diameter of can be designed large.

Specifically, when the tip seal 82 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, the diameter of the injection port 63 is set to “(wrap The restriction value must be equal to or less than “part width / 2) + (tip seal width / 2)”. In the compressor 100, a tip seal 82 is integrally formed by connecting three curve portions of a first curve portion 82a having the above configuration, a second curve portion 82b, and a third curve portion 82c. Therefore, the diameter of the injection port 63 can be expanded beyond the restriction value.

As a result, in the compressor 100, the resistance when the working gas is discharged from the sub port 62 is reduced, and the performance can be improved. Further, in the compressor 100, when the injection port 63 is formed instead of the sub port 62, the flow rate of the liquid phase working fluid to be injected is increased, and the discharge temperature can be lowered more efficiently.

In addition, for example, when the chip seal is provided with a notch as in the prior art, gas leakage from the notch to the adjacent compression chamber may occur, which may significantly reduce the performance of the compressor. Furthermore, the stress concentration in the notch of the tip seal may reduce the strength of the tip seal. In the compressor 100, the tip seal 82 is disposed at a position away from the sub port 62 or the injection port 63, and the tip 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 oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 are fixed respectively to the oscillating scroll wrap 71 It is disposed at the center 71 a of the tip end surface of the spiral wrap portion 61. Therefore, in the conventional compressor, the tip seal 80 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 are alternately attached, which may cause an assembly failure. On the other hand, in the compressor 100, the tip seal 82 is integrally formed by connecting three curve portions of the first curve portion 82a, the second curve portion 82b, and the third curve portion 82c having the above configuration. It is done. In the compressor 100, when the tip seal 80 of the fixed scroll 60 is formed by an involute curve as in the conventional case and disposed at the center 71a of the tip surface of the fixed spiral wrap portion 61, the tip seal 80 of the fixed scroll 60 and the oscillating scroll 70 The shape of the tip seal 82 is different. Therefore, the compressor 100 can prevent the tip seal 82 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled by mistake.

Further, since the tip seal 82 of the compressor 100 smoothly connects a plurality of curves, in the swing scroll 70, the fitting groove of the tip seal 82 can be processed at a time by a single stroke, which is an excellent process It is possible to secure the sex.

Second Embodiment
FIG. 7 is an axial sectional view showing the shapes of the oscillating scroll 70, the fixed scroll 60, and the tip seal 83 in the compressor 110 according to Embodiment 2 of the present invention. The parts having the same configuration as that of the compressor 100 in FIGS. 1 to 6 are denoted by the same reference numerals, and the description thereof will be omitted. The compressor 110 is the same as the compressor 100 except that the configuration of the tip seal 83 is different from that 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 end face of the fixed scroll 60 and the oscillating scroll 70. The tip seal 83 is fitted in the tip seal fitting groove 81. It is done. The tip seal 83 of the rocking scroll 70 is disposed along the spiral direction at the tip of the rocking scroll wrap portion 71 and contacts the fixed scroll base plate portion 64 of the fixed scroll 60 facing it. Further, a tip seal 83 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip end of the fixed spiral wrap portion 61 and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing. The tip seal 83 slides while being pressed against the stationary scroll base plate portion 64 while the compressor 110 is in operation, so that the gap between the oscillating scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 83 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 110 is in operation, so that the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 is fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 a tip seal 83 provided on the wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 83, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 83 is not completely crossed.

In the compressor 110, as shown in FIG. 7, the tip seal 83 is composed of a plurality of curves having different curvatures, and two curve portions of a first curve portion 83a and a second curve portion 83b are It is connected together and is constituted in one. Although the tip seal 83 is illustrated as having a cut in order to clearly show the boundary of the curve in FIG. 7, the boundary of the two curves is not divided, and the tip seal 83 is a single piece without a break. is there. That is, in the tip seal 83, a plurality of curves having different curvatures are continuously formed. With respect to the tip seal 83, the portion approaching the sub port 62 or the injection port 63 is on the side of the end edge 71b on the outer periphery and the side of the end edge 71c on the inner periphery with respect to the center 71a in the width direction of the swing scroll wrap 71 It is arranged.

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

The tip seal 83 is formed of an involute curve having a curvature larger than that of the swinging scroll 70, and has a second curve portion 83b disposed closer to the inside of the swinging scroll wrap 71 as it approaches the spiral center. In the second curved portion 83b of the tip seal 83, the portion approaching the sub-port 62b on the inward facing surface side of the fixed scroll 60 is the end edge 71c side of the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. Pass through. Alternatively, in the second curved portion 83b of the tip seal 83, the portion approaching the injection port 63b on the inward surface side of the fixed scroll 60 is an edge of the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. Pass the part 71c side.

In the compressor 110 according to the second embodiment, the tip seal 83 is formed of two curve portions, but the number of curve portions constituting the tip seal 83 is changed according to the number of sub ports 62 or injection ports 63. Needless to say, 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 scroll wrap portion 61 of the fixed scroll 60 as before, and the center 71 a in the width direction of the fixed scroll wrap portion 61 of the fixed scroll 60 It may be arranged in

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 the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap 71 It is arrange | positioned at the edge part 71c side of inner periphery. That is, the sub-ports 62a on the outward facing surface side of the fixed scroll 60 of the tip seal 83 and the sub-ports 62b on the inward facing surface side of the fixed scroll 60 move away from the subport 62 with respect to the center 71a of the oscillating scroll wrap 71, respectively. It is arranged on the side. Therefore, the compressor 110 can secure a larger seal width δ as compared with the case where the tip seal 83 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the sub port 62 The diameter can be designed large.

Specifically, when the tip seal 83 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, the diameter of the subport 62 is set to “(wrap portion to satisfy seal width δ> 0 The constraint value must be equal to or less than width / 2) + (tip seal width / 2). On the other hand, 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, the sub port is not less than this restriction value. It is possible to enlarge the diameter of 62.

Further, the injection port 63 can be designed to be large similarly for the compressor 110 in which the injection port 63 is provided instead of the sub port 62. In the compressor 110, the injection port 63 a of the tip seal 83 and the portions approaching the injection port 63 b are disposed on the side away from the injection port 63 with respect to the center 71 a of the oscillating scroll wrap portion 71. Therefore, the compressor 110 can secure a large seal width δ as compared with the case where the tip seal 83 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the injection port 63. The diameter of can be designed large.

Specifically, when the tip seal 83 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, the diameter of the injection port 63 is set to “(wrap The restriction value must be equal to or less than “part width / 2) + (tip seal width / 2)”. In the compressor 110, since the tip seal 83 is integrally formed by connecting two curve portions of the first curve portion 83a having the above configuration and the second curve portion 83b, the injection is performed in excess of this restriction value. The diameter of the port 63 can be enlarged.

As a result, the resistance of the compressor 110 when the working gas is discharged from the sub port 62 is reduced, and the performance can be improved. Further, when 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 the chip seal is provided with a notch as in the prior art, gas leakage from the notch to the adjacent compression chamber may occur, which may significantly reduce the performance of the compressor. Furthermore, the stress concentration in the notch of the tip seal may reduce the strength of the tip seal. The compressor 110 is disposed at a position where the tip seal 83 is separated from the sub port 62 or the injection port 63, and the tip 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 connecting two curve portions of a first curve portion 83a having the above configuration and a second curve portion 83b. 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 oscillating scroll 70 when arranging the tip seal 80 at the center 71 a of the tip surface of the fixed spiral wrap portion 61. The shape of the tip seal 83 is different. Therefore, the compressor 110 can prevent the tip seal 83 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled by mistake in an alternate manner.

Further, since the tip seal 83 of the compressor 110 smoothly connects a plurality of curves, in the swing scroll 70, the fitting groove of the tip seal 83 can be processed at a time by one-stroke writing, which is excellent processing It is possible to secure the sex.

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. Therefore, when processing the fitting groove of the tip seal 83 on the front end surface of the swing scroll wrap portion 71, the compressor 110 reduces the boundary forming the groove, and the fitting groove of the tip seal 83 is formed at this boundary. It becomes difficult to cause processing problems such as step differences.

Third Embodiment
FIG. 8 is an axial sectional view showing the shapes of the oscillating 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 configurations as those of 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 configuration of the tip seal 84 of the compressor 120 is different from that of the tip seal 82 of the compressor 100, and the other configuration of the compressor 120 is the same as that of the compressor 100.

A tip seal fitting groove 81 having the same shape as the tip seal 84 is formed on the wrap tip end surface of the fixed scroll 60 and the oscillating scroll 70, and the tip seal 84 is fitted in the tip seal fitting groove 81. It is done. The tip seal 84 of the oscillating scroll 70 is disposed along the spiral direction at the tip of the oscillating scroll wrap 71 and contacts the fixed scroll base plate 64 of the fixed scroll 60 facing it. Further, a tip seal 84 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip end of the fixed spiral wrap portion 61 and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing it. The tip seal 84 slides while being pressed against the stationary scroll base plate portion 64 while the compressor 120 is in operation, so that the gap between the oscillating scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 84 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 120 is in operation, so that the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 is fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 a tip seal 84 provided on the wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 84, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 84 is not completely crossed.

In the compressor 120, as shown in FIG. 8, the tip seal 84 is composed of a plurality of curves having different curvatures, and a first curve portion 84a, a second curve portion 84b, and a third curve portion 84c. , And a fourth curved portion 84d and a fifth curved portion 84e. In the compressor 120, as shown in FIG. 8, the tip seal 84 has 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. The five curve parts of are connected together to form an integral unit. Although the tip seal 84 is illustrated as having a cut in order to clearly show the boundary of the curve in FIG. 8, the boundary of the five curves is not divided, and the tip seal 84 is a single piece 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 is a first curved portion 84 a where the portion approaching the subport 62 a on the outward surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing scroll wrap portion 71. Have. Alternatively, in the tip seal 84, the portion approaching the injection port 63 a on the outward facing surface side of the fixed scroll 60 passes the side of the end edge 71 b on the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It has a curved portion 84a. The first curve portion 84 a is formed of, for example, an involute curve having the same curvature as the swing spiral wrap portion 71 of the swing scroll 70.

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

The boundary between the first curve portion 84a and the second curve portion 84b is joined together by a third curve portion 84c formed into a smooth curve, such as an involute curve having a curvature larger than that of the oscillating scroll 70, for example. The fourth curve portion 84d of the tip seal 84 connects the end portions of the first curve portion 84a and the fifth curve portion 84e, which are adjacent curves, smoothly using an involute curve or the like having a smaller pitch than the swing scroll 70. There is. The fifth curved portion 84 e of the tip seal 84 is formed by an involute curve passing through the center of the swinging spiral wrap portion 71.

In the compressor 120 according to the third embodiment, the tip seal 84 is formed of five curve portions, but the number of curve portions constituting the tip seal 84 is changed according to the number of sub ports 62 or injection ports 63. Needless to say, it is good. 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 scroll wrap portion 61 of the fixed scroll 60 as before, and the center 71 a in the width direction of the fixed scroll wrap portion 61 of the fixed scroll 60 It may be arranged in

As described above, in the tip seal 84 of the compressor 120, the portion approaching the sub port 62 or the injection port 63 is the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap 71 It is arrange | positioned at the edge part 71c side of inner periphery. That is, the sub-ports 62a on the outward facing surface side of the fixed scroll 60 of the tip seal 84 and the sub-ports 62b on the inward facing surface side of the fixed scroll 60 are separated from the subport 62 with respect to the center 71a of the oscillating scroll wrap 71, respectively. It is arranged on the side. Therefore, the compressor 120 can secure a larger seal width δ as compared with the case where the tip seal 84 is configured in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the sub port 62 The diameter can be designed large.

Specifically, when the tip seal 84 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the conventional case, the diameter of the subport 62 is set to “(wrap portion to satisfy seal width δ> 0 The constraint value must be equal to or less than width / 2) + (tip seal width / 2). On the other hand, in the compressor 120, the tip seal 84 has five of 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. The curved portions are connected together to form an integral unit. Therefore, the compressor 120 can enlarge the diameter of the sub port 62 more than this restriction value.

Further, the injection port 63 can be designed to be large similarly for the compressor 120 in which the injection port 63 is provided instead of the sub port 62. The compressor 120 is disposed on the side of the tip seal 84 where the injection port 63 a and the injection port 63 b approach each other with respect to the center 71 a of the swing scroll wrap portion 71 away from the injection port 63. Therefore, the compressor 120 can secure a large seal width δ as compared with the case where the tip seal 84 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the injection port 63 The diameter of can be designed large.

Specifically, when the tip seal 84 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, in order to satisfy the seal width δ> 0, the diameter of the injection port 63 The restriction value must be equal to or less than “part width / 2) + (tip seal width / 2)”. In the compressor 120, the tip seal 84 has five components, a first curve portion 84a having the above configuration, a second curve portion 84b, a third curve portion 84c, a fourth curve portion 84d, and a fifth curve portion 84e. The curved portions are connected together to form an integral unit. Therefore, the compressor 120 can enlarge the diameter of the injection port 63 more than this restriction value.

As a result, the resistance of the compressor 120 when the working gas is discharged from the sub port 62 is reduced, and the performance can be improved. Further, in the compressor 120, when the injection port 63 is formed instead of the sub port 62, the flow rate of the liquid phase working fluid to be injected is increased, and the discharge temperature can be lowered more efficiently.

Further, for example, when the chip seal is provided with a notch as in the prior art, gas leakage from the notch to the adjacent compression chamber may occur, which may significantly reduce the performance of the compressor. Furthermore, the stress concentration in the notch of the tip seal may reduce the strength of the tip seal. The compressor 120 is disposed at a position where the tip seal 84 is separated from the sub port 62 or the injection port 63, and the tip 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 is not reduced 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 curve parts are connected together and configured integrally. The compressor 120 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the prior art and arranges the tip seal 80 of the fixed scroll 60 and the oscillating scroll 70 when arranging the tip seal 80 at the center 71 a of the tip surface of the fixed spiral wrap portion 61. The shape of the tip seal 84 is different. Therefore, the compressor 120 can prevent the tip seal 84 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled by mistake in an alternate manner.

Further, since the tip seal 84 of the compressor 120 smoothly connects a plurality of curves, in the swing scroll 70, the fitting groove of the tip seal 84 can be processed at a time by one-stroke writing, which is excellent processing It is possible to secure the sex.

Generally, in the end face of the spiral wrap, a portion where the tip seal is not fitted is a leak flow path between adjacent compression chambers. If the tip seal is offset from the center of the tip end face of the wrap, pressure leakage will occur in the two compression chambers in symmetrical positions due to different leak flow rates between the inside and the outside of the tip seal. The unbalance of pressure generates a force to rotate the spiral, which may affect the reliability of the spiral and the Oldham ring 41. On the other hand, in the tip seal 84 of the compressor 120, the fourth curve portion 84d and the fifth curve portion 84e located on the outer side of the first curve portion 84a approaching the subport 62a of the fixed scroll 60 on the outward surface side. Are disposed at the center 71 a of the swing scroll wrap 71. Therefore, in the compressor 120, since the width of both sides of the fitting groove of the tip seal 84 formed in the swinging scroll wrap portion 71 is equal, the leakage amount of the symmetrical compression chamber becomes uniform, and the swinging scroll 70 movements are stable and high reliability can be obtained.

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

A tip seal fitting groove 81 having the same shape as the tip seal 85 is formed on the wrap tip end face of the fixed scroll 60 and the oscillating scroll 70, and the tip seal 85 is fitted in the tip seal fitting groove 81. It is done. The tip seal 85 of the rocking scroll 70 is disposed along the spiral direction at the tip of the rocking scroll wrap 71 and contacts the fixed scroll base plate 64 of the fixed scroll 60 facing it. Further, a tip seal 85 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip of the fixed spiral wrap portion 61, and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing it. The tip seal 85 slides while being pressed against the stationary scroll base plate portion 64 while the compressor 130 is in operation, so that the gap between the oscillating scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 85 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 130 is in operation, so that the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 is fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 a tip seal 85 provided on the wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 85, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 85 is not completely crossed.

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

The tip seal 85 is a first curved portion 85 a where the portion approaching the subport 62 a on the outward facing surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. Have. Alternatively, the tip seal 85 may be configured such that the portion approaching the injection port 63 a on the outward facing surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It has a curved portion 85a. The first curve portion 85 a is formed of an involute curve having the same curvature as the swing spiral wrap portion 71 of the swing scroll 70.

The tip seal 85 is a second curved portion in which the portion approaching the subport 62b on the inward facing surface side of the fixed scroll 60 passes the end edge 71c side of the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It has 85b. Alternatively, in the tip seal 85, the portion approaching the injection port 63b on the inward facing surface side of the fixed scroll 60 passes through the end edge 71c on the inner periphery with respect to the center 71a in the width direction of the swing spiral wrap portion 71. It has a two-curved portion 85b. The second curve portion 85 b is formed of an involute curve having the same curvature as the swing spiral wrap portion 71 of the swing scroll 70.

In the compressor 130 according to the fourth embodiment, the tip seal 85 is formed of two curved portions, but the number of curved portions constituting the tip seal 85 is changed according to the number of sub ports 62 or injection ports 63. Needless to say, it is good. 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 scroll wrap portion 61 of the fixed scroll 60 as before, and the center 71 a in the width direction of the fixed scroll wrap portion 61 of the fixed scroll 60 It may be arranged in

As described above, in the tip seal 85 of the compressor 130, the portion approaching the sub port 62 or the injection port 63 is the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It is arrange | positioned at the edge part 71c side of inner periphery. That is, the sub-ports 62a on the outward facing surface side of the fixed scroll 60 of the tip seal 85 and the sub-ports 62b on the inward facing surface side of the fixed scroll 60 are separated from the subport 62 with respect to the center 71a of the oscillating scroll wrap 71, respectively. It is arranged on the side. Therefore, the compressor 130 can secure a larger seal width δ as compared with the case where the tip seal 85 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the subport 62 The diameter can be designed large.

Specifically, when the tip seal 85 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, the diameter of the subport 62 is set to “(wrap portion to satisfy seal width δ> 0 The constraint value must be equal to or less than 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 a first curved portion 85a and a second curved portion 85b. Therefore, the compressor 130 can enlarge the diameter of the subport 62 more than this restriction value.

Further, the injection port 63 can be designed to be large similarly for the compressor 130 in which the injection port 63 is provided instead of the sub port 62. In the compressor 130, the injection port 63 a of the tip seal 85 and the portions approaching the injection port 63 b are disposed on the side away from the injection port 63 with respect to the center 71 a of the oscillating scroll wrap portion 71. Therefore, the compressor 130 can secure a large seal width δ as compared with the case where the tip seal 85 is configured in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the injection port 63 The diameter of can be designed large.

Specifically, when the tip seal 85 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the prior art, the diameter of the injection port 63 is set to “(wrap The restriction value must be equal to or less than “part width / 2) + (tip seal width / 2)”. The compressor 130 is configured such that the tip seal 85 includes two curved portions, a first curved portion 85a having the above configuration and a second curved portion 85b. Therefore, the compressor 130 can enlarge the diameter of the injection port 63 more than this restriction value.

Thereby, the resistance at the time of discharge of the working gas from the sub port 62 is reduced, and the performance of the compressor 130 can be improved. Further, when the injection port 63 is formed instead of the sub port 62, the compressor 130 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 the chip seal is provided with a notch as in the prior art, gas leakage from the notch to the adjacent compression chamber may occur, which may significantly reduce the performance of the compressor. Furthermore, the stress concentration in the notch of the tip seal may reduce the strength of the tip seal. The compressor 130 is disposed at a position where the tip seal 85 is separated from the sub port 62 or the injection port 63, and the tip 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 curve portions of a first curve portion 85a having the above configuration and a second curve portion 85b. The compressor 130 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the prior art and arranges the tip seal 80 of the fixed scroll 60 and the oscillating scroll 70 when arranging the tip seal 80 at the center 71 a of the tip surface of the fixed spiral wrap portion 61. The shape of the tip seal 85 is different. Therefore, the compressor 130 can prevent the tip seal 85 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled by mistake in an alternate manner.

According to the compressor 130 according to the fourth embodiment, since there is no joint of different curve in the fitting groove of the tip seal 85 provided in the swinging scroll wrap portion 71, the processing is easy. Therefore, in the compressor 130, a manufacturing defect such as a level difference at the boundary of the curve of the fitting groove of the tip seal 85 does not occur. In addition, the compressor 130 facilitates the production of a die for the tip seal 85.

Embodiment 5
FIG. 10 is an axial sectional view showing the shapes of the orbiting scroll 70, the fixed scroll 60 and the tip seal 86 in the 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 the 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 that 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 wrap tip end surface of the fixed scroll 60 and the oscillating scroll 70. The tip seal 86 is fitted in the tip seal fitting groove 81. It is done. The tip seal 86 of the rocking scroll 70 is disposed at the tip of the rocking scroll wrap 71 along the spiral direction, and contacts the fixed scroll base plate 64 of the fixed scroll 60 facing it. Further, a tip seal 86 (not shown) of the fixed scroll 60 is disposed along the spiral direction at the tip of the fixed spiral wrap portion 61 and contacts the swing scroll base plate portion 74 of the swing scroll 70 facing. The tip seal 86 slides while being pressed against the stationary scroll base plate portion 64 while the compressor 140 is in operation, so that the gap between the swinging scroll wrap portion 71 and the stationary scroll base plate portion 64 and the stationary scroll wrap portion The gap between the upper portion 61 and the swinging swirl wrap portion 71 is filled to prevent the leakage of the working gas. Alternatively, the tip seal 86 slides while being pressed against the swing scroll bed plate portion 74 while the compressor 140 is in operation, whereby the gap between the fixed scroll wrap portion 61 and the swing scroll bed plate portion 74 and the fixing are fixed. The gap between the spiral wrap portion 61 and the swing spiral wrap portion 71 is filled to prevent the 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 a tip seal 86 provided on the wrap tip end surface of the oscillating scroll 70. In order to ensure the sealability of the tip seal 86, the diameter of the sub port 62 or the injection port 63 needs to be set within a range in which the tip seal 86 is not completely crossed.

In the compressor 140, the tip seal 86 of the oscillating scroll 70 is formed of a plurality of curves having different curvatures, and is configured to have an involute portion 86a and an R portion 86b. The tip seal 86 is formed by continuously forming a plurality of curves having different curvatures. The R portion 86 b of the tip seal 86 is disposed at a position approaching the sub port 62 or the injection port 63, and is formed in a curved arc shape so as to avoid the sub port 62 or the injection port 63. The tip seal 86 is configured such that the portion other than the R portion 86 b is an involute portion 86 a. The involute portion 86 a is disposed on the wrap tip end surface of the oscillating scroll 70 and is formed of an involute curve having the same curvature as that of the oscillating scroll wrap portion 71 through the center 71 a in the width direction of the oscillating scroll 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 86 b 1 where the portion approaching the subport 62 a on the outward facing surface side of the fixed scroll 60 passes the side of the end edge 71 b of the outer periphery with respect to the center 71 a in the width direction of the swing scroll wrap 71 . Alternatively, the tip seal 86 has a portion where the portion approaching the injection port 63 a on the outward facing surface side of the fixed scroll 60 passes the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap portion 71. It has 86b1.

In the tip seal 86, the R portion 86b2 passes through the end portion 71c on the inner circumferential side with respect to the center 71a in the width direction of the swing scroll wrap portion 71 at a location where the tip seal 86 approaches the subport 62b on the inward facing side Have. Alternatively, the tip seal 86 has a location where an injection port 63 b on the inward surface side of the fixed scroll 60 approaches the end edge 71 c on the inner periphery with respect to the center 71 a in the width direction of the swing scroll wrap 71 It has a portion 86b2.

In the compressor 140 according to the fifth embodiment, the tip seal 86 includes two R portions 86 b, but the number of R portions 86 b constituting the tip seal 86 according to the number of sub ports 62 or injection ports 63. It goes without saying that it is good to change. The shape of the tip seal 86 of the fixed scroll 60 is formed by an involute curve having the same curvature as that of the fixed scroll wrap portion 61 of the fixed scroll 60 as before, and the center 71 a in the width direction of the fixed scroll wrap portion 61 of the fixed scroll 60 It may be arranged in

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 the end edge 71 b side of the outer periphery with respect to the center 71 a in the width direction of the swing spiral wrap 71 It is arrange | positioned at the edge part 71c side of inner periphery. That is, portions of the tip seal 86 closer to the subport 62a on the outward facing surface side of the fixed scroll 60 and the subport 62b on the inward facing surface side of the fixed scroll 60 separate from the subport 62 with respect to the center 71a of the oscillating scroll wrap portion 71. It is arranged on the side. Therefore, the compressor 140 can secure a larger seal width δ as compared with the case where the tip seal 86 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the subport 62 The diameter can be designed large.

Specifically, when the tip seal 86 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the conventional case, the diameter of the subport 62 is set to “(wrap portion to satisfy seal width δ> 0 The constraint value must be equal to or less than width / 2) + (tip seal width / 2). On the other hand, in the compressor 140, the tip seal 86 is configured to include an R portion 86b curved 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 enlarge the diameter of the sub port 62 more than this restriction value.

Further, the injection port 63 can be designed to be large similarly for the compressor 140 in which the injection port 63 is provided instead of the sub port 62. The compressor 140 is disposed on the side of the tip seal 86 where the injection port 63 a and the injection port 63 b approach each other with respect to the center 71 a of the swing scroll wrap portion 71 away from the injection port 63. Therefore, the compressor 140 can secure a large seal width δ as compared with the case where the tip seal 86 is formed in one involute shape and disposed at the center 71 a of the swing scroll wrap portion 71, and the injection port 63. The diameter of can be designed large.

Specifically, when the tip seal 86 is disposed at the center 71 a of the tip end surface of the swing scroll wrap portion 71 as in the conventional case, the diameter of the injection port 63 is set to “(wrap The restriction value must be equal to or less than “part width / 2) + (tip seal width / 2)”. In the compressor 140, the tip seal 86 includes an R portion 86b curved 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 enlarge the diameter of the injection port 63 more than this restriction value.

As a result, the resistance of the compressor 140 when the working gas is discharged from the sub port 62 is reduced, and the performance 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 the chip seal is provided with a notch as in the prior art, gas leakage from the notch to the adjacent compression chamber may occur, which may significantly reduce the performance of the compressor. Furthermore, the stress concentration in the notch of the tip seal may reduce the strength of the tip seal. The compressor 140 is disposed at a position where the tip seal 86 is separated from the sub port 62 or the injection port 63, and the tip 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 is not reduced due to stress concentration.

Further, the compressor 140 is configured to have a tip seal 86 including an R portion 86 b curved in an arc shape so as to avoid the sub port 62 or the injection port 63 and an involute portion 86 a. The compressor 140 forms the tip seal 80 of the fixed scroll 60 with an involute curve as in the prior art and arranges the tip seal 80 of the fixed scroll 60 and the oscillating scroll 70 when arranging the tip seal 80 at the center 71 a of the tip surface of the fixed spiral wrap portion 61. The shape of the tip seal 86 is different. Therefore, the compressor 140 can prevent the tip seal 86 of the oscillating scroll 70 and the tip seal 80 of the fixed scroll 60 from being assembled by mistake in an alternate manner.

The compressor 140 also has an R portion 86 b which is curved in an arc shape so as to avoid the sub port 62 or the injection port 63. Therefore, the compressor 140 can arrange the tip seal 86 away from the sub port 62 or the injection port 63 only in the minimum range approaching the sub port 62 or the injection port 63. In the compressor 140, the involute portion 86 a is disposed at the center 71 a of the tip end surface of the swinging scroll wrap portion 71 in places other than the R portion 86 b. Therefore, the compressor 140 has high reliability because the unbalance of the leak amount between the inside and the outside of the tip seal 86 is minimized and the unbalance of the pressure of the compression chamber in the symmetrical position is also minimized. Be

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

Reference Signs List 20 shell, 20a lower shell, 20b central shell, 20c upper shell, 21 oil reservoir, 23 oil pump, 24 oil discharge pipe, 25 frame, 25a suction port, 26 subframe, 27 suction pipe, 28 discharge pipe, 29 muffler, 30 Motor, 31 rotor, 32 stator, 40 compression unit, 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 portion , 50a oil supply passage, 52 first balancer, 52a balancer cover, 53 second balancer, 54 main bearing, 55 secondary bearing, 60 fixed scroll, 61 fixed scroll wrap portion, 62 subport, 62a subport, 62b subport, Reference Signs List 3 injection port, 63a injection port, 63b injection port, 64 fixed scroll base plate portion, 65 discharge port, 70 rocking scroll, 71 rocking scroll wrap portion, 71a center, 71b end edge, 71c end edge, 74 rocking Moving scroll base plate section 80 chip seal 81 chip seal fitting groove 82 chip seal 82a first curve section 82b second curve section 82c third curve section 83 chip seal 83a first curve section 83b Second curve section, 84 tip seal, 84a first curve section, 84b second curve section, 84c third curve section, 84d fourth curve section, 84e fifth curve section, 85 tip seal, 85a first curve section, 85b Second curve, 86 tip seal, 86a involute, 86 R unit, 86B1 R unit, 86B2 R unit, 100 compressor, 110 compressor, 120 compressor, 130 compressor, 140 compressor.

Claims

A fixed scroll provided with a base plate portion and a spiral wrap portion formed on the base plate portion;
A swinging scroll provided with a base plate portion and a spiral wrap portion formed on the base plate portion;
Have
The fixed scroll is formed with at least one subport for discharging a working gas, or at least one injection port for injecting a working fluid in a liquid phase,
The oscillating scroll is
The tip end of the spiral wrap portion includes a tip seal disposed along the spiral direction and in contact with the base plate portion of the fixed scroll facing the tip end.
The said tip seal is a compressor by which the location which approaches the said subport or the said injection port is arrange | positioned with respect to the center of the width direction of the said spiral wrap part at the edge part side.
The compressor according to claim 1, wherein the tip seal comprises a plurality of curves having different curvatures.
The compressor according to claim 2, wherein the tip seal is formed by continuously forming a plurality of curves having different curvatures.
The compressor according to claim 2, wherein the tip seal is divided into a plurality of curves having different curvatures.
The tip seal is
The portion according to any one of claims 1 to 4, wherein the portion approaching the sub port or the injection port has a first curve portion passing an end edge side of the outer periphery with respect to the widthwise center of the spiral wrap portion. Compressor.
The compressor according to claim 5, wherein the first curve portion is formed of an involute curve having the same curvature as that of the spiral wrap portion.
The tip seal is
7. The second curved portion according to any one of claims 1 to 6, wherein the portion approaching the sub port or the injection port has a second curved portion passing the end edge side of the inner periphery with respect to the widthwise center of the spiral wrap portion. Description compressor.
The compressor according to claim 7, wherein the second curve portion is formed of an involute curve having the same curvature as that of the spiral wrap portion.
The compressor according to claim 7, wherein the second curve portion is formed of an involute curve having a curvature larger than that of the spiral wrap portion.
The tip seal is
The compressor according to any one of claims 5 to 9, further comprising a third curve portion formed of an involute curve having a curvature larger than that of the spiral wrap portion.
The tip seal is
The compressor according to claim 10, further comprising a fourth curve portion formed of an involute curve having a curvature smaller than that of the spiral wrap portion.
The tip seal is
The compressor according to claim 11, further comprising a fifth curve portion passing through the center in the width direction of the spiral wrap portion.
The tip seal is
The portion approaching the sub port or the injection port is curved and formed into 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 part.
The fixed scroll is
The tip end of the spiral wrap portion is provided along a spiral direction, and includes a tip seal in contact with the base plate portion of the swinging scroll facing the tip portion.
The tip seal of the fixed scroll is formed of 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. The compressor according to any one of the items.