JP2018173036A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor capable of reducing the installation positions of gas injection ports while suppressing a reduction in the total supply amount of refrigerant from the gas injection ports to an inside compression chamber and an outside compression chamber.SOLUTION: An inside compression chamber 10a has a gentler volumetric change with the turning movement of a turning scroll 11, than an outside compression chamber 10b. Intermediate pressure ports 125 as the gas injection ports are arranged at sites to be communicated with the inside compression chamber 10a for a longer time than with the outside compression chamber 10b, out of a fixed base surface 121a. So, compared with the case that the intermediate pressure ports 125 are not arranged in such a way, a total period for the intermediate pressure ports 125 to open to each of the compression chambers 10a, 10b can be longer. This reduce the installation positions of the intermediate pressure ports 125 while suppressing a reduction in the total supply amount of the refrigerant from the intermediate pressure ports 125.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a scroll compressor that discharges after compressing a fluid.

  As this type of scroll compressor, for example, a scroll compressor described in Patent Document 1 is conventionally known. The scroll compressor described in Patent Document 1 is a compressor used in a gas injection cycle. Therefore, this scroll compressor has one injection port for injecting an intermediate pressure refrigerant into the compression chamber.

  Moreover, the scroll compressor of patent document 1 has a fixed scroll and a turning scroll, and the wrap winding angle of the fixed scroll is larger than the wrap winding angle of the turning scroll. Therefore, the scroll compressor of patent document 1 Is an asymmetric scroll compressor.

  Further, the injection port is disposed at a position separated from the wrap of the fixed scroll by a wrap thickness and not leading to the suction port. Thereby, although there is one injection port, the refrigerant is alternately injected from the one injection port into the inner compression chamber formed on the inner side and the outer compression chamber formed on the outer side with respect to the orbiting scroll wrap. Is possible.

  Further, the injection port is arranged at a position where the refrigerant is injected over a long time into the compression chamber having the smaller sealed volume than the larger one of the two compression chambers. According to Patent Document 1, such an arrangement is effective for improving the efficiency of the scroll compressor.

Japanese Patent No. 4265128

  In the scroll compressor of Patent Document 1, the two compression chambers, which are the inner compression chamber and the outer compression chamber, sequentially start compressing the refrigerant as the orbiting scroll moves. Specifically, between the compression chamber that starts compression first and the compression chamber that starts compression later, compression starts at a position where the turning angle position of the orbiting scroll is shifted by about 180 degrees. Is done. In such an asymmetric scroll compressor, the timing at which one injection port communicates with each of the two compression chambers is also shifted by approximately 180 degrees at the turning angle position of the turning scroll. For this reason, the asymmetric scroll compressor has a good compatibility with a single injection port instead of a plurality.

  However, in general, many scroll compressors are symmetrical scroll compressors that start compression in the inner compression chamber and the outer compression chamber simultaneously or substantially simultaneously. In such a symmetrical scroll compressor, the suction volume of the inner compression chamber and the suction volume of the outer compression chamber are approximately the same. Then, if the refrigerant is injected into each of the inner compression chamber and the outer compression chamber with one injection port, the gas injection into the compression chamber on the side to be injected later is normally performed between the two compression chambers. The amount will be insufficient. This is because the refrigerant pressure in the compression chamber becomes too high in the compression chamber on the side that is injected later, and a sufficient pressure difference for performing injection cannot be obtained.

  For this reason, a symmetrical scroll compressor is usually provided with two injection ports, one for the inner compression chamber and one for the outer compression chamber. As a result, the structure of the compressor is complicated. As a result of detailed studies by the inventors, the above has been found.

  In view of the above, the present invention provides a scroll compressor capable of reducing the number of gas injection port installation locations while suppressing a decrease in the total amount of fluid supplied from the gas injection port to the inner compression chamber and the outer compression chamber. The purpose is to do.

In order to achieve the above object, a scroll compressor according to claim 1,
A scroll compressor that discharges after compressing the fluid,
A fixed scroll (12) having a fixed base part (121) and a fixed tooth part (122) projecting from the fixed base part and having a spiral shape;
An orbiting scroll (11) having an orbiting base portion (111) and an orbiting tooth portion (112) projecting from the orbiting base portion and having a spiral shape, and orbiting about a single axis (C1) with respect to the fixed scroll And
The fixed tooth portion and the swivel tooth portion engage with each other, and are located on the radially inner side of the swivel tooth portion and compress the fluid, and located on the radially outer side of the swivel tooth portion and compress the fluid. Forming an outer compression chamber (10b) between the fixed tooth part and the swivel tooth part,
The orbiting scroll moves the inner compression chamber and the outer compression chamber radially inward along with the orbiting movement of the orbiting scroll and reduces the volume of the inner compression chamber and the volume of the outer compression chamber,
One compression chamber of the inner compression chamber and the outer compression chamber changes in volume more slowly than the other compression chamber as the orbiting scroll revolves.
The fixed base portion has a fixed base surface (121a) that is formed between the fixed tooth portions and faces the front end surface (112c) of the swivel tooth portion. The fixed base surface is covered with the front end surface of the swivel tooth portion. A gas injection port (125) that is blocked by
Gas injection port
Do not communicate with the inner and outer compression chambers at the same time,
Communicating at least one of the inner compression chamber and the outer compression chamber for each rotation of the orbiting scroll, and joining fluid from the outside to the fluid being compressed in the communication compression chamber;
It arrange | positions among the fixed base | substrate surfaces in the site | part connected to one compression chamber for a long time rather than the other compression chamber.

  In this case, on the contrary, the gas injection port is, for example, compared with the case where the gas injection port is arranged in a portion of the fixed base surface that communicates with the other compression chamber for a longer time than the one compression chamber. It is possible to lengthen the total period of opening to each of the compression chambers. Therefore, it is possible to reduce the number of installation locations of the gas injection port while suppressing a decrease in the total amount of fluid supplied from the gas injection port to the inner compression chamber and the outer compression chamber. For example, the gas injection port can be installed at one location while suppressing a decrease in the total supply amount of the fluid. The scroll compressor may be either a symmetric scroll compressor or an asymmetric scroll compressor.

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

It is the circuit diagram which showed schematic structure of the refrigerating cycle in 1st Embodiment. It is sectional drawing which cut | disconnected the compressor of 1st Embodiment in the plane containing a compressor shaft center. It is sectional drawing which showed the cross section which cut | disconnected the compression mechanism part which the compressor of 1st Embodiment has with the plane orthogonal to a compressor shaft center, ie, sectional drawing which showed the III-III cross section of FIG. FIG. 4 is a cross-sectional view showing the IV-IV cross section of FIG. 3, and in detail, a partial cross-section showing a part extracted from a cross section cut along a plane whose normal direction is the tangential direction of the spiral shape of the fixed tooth portion FIG. In the compressor of 1st Embodiment, it is the operation | movement figure which each represented the relative positional relationship of the turning scroll with respect to a fixed scroll in the several turning angle position of a turning scroll. FIG. 4 is a cross-sectional view showing a VI-VI cross section of FIG. 3, and in detail, a partial cross-section showing a part extracted from a cross section cut along a plane in which the tangential direction of the spiral shape of the fixed tooth portion is a normal direction. FIG. In the compressor of 1st Embodiment, it is the figure which showed the relationship between each of the volume of an inner side compression chamber, the volume of an outer side compression chamber, and those total volumes, and the turning angle position of a turning scroll. In the compressor of 1st Embodiment, it is the figure which showed the relationship between each of the pressure of an inner side compression chamber, the pressure of an outer side compression chamber, and the pressure after the unification | combination of both compression chambers, and the turning angle position of a turning scroll. FIG. 4 is a diagram showing a port arrangement region and three virtual ports assumed as intermediate pressure ports in the same sectional view as FIG. 3. FIG. 10 is a virtual cross-sectional view showing the radial positions of the three virtual ports by displaying the three virtual ports of FIG. 9 side by side in a cross section along the radial direction of the fixed scroll. In 1st Embodiment, it is the figure which showed the relationship between the opening area of the inner side port of FIG. 9 with respect to an inner side compression chamber, and the turning angle position of a turning scroll. In 1st Embodiment, it is the figure which showed the relationship between the opening area of the center port of FIG. 9 with respect to each of an inner side compression chamber and an outer side compression chamber, and the turning angle position of a turning scroll. In 1st Embodiment, it is the figure which showed the relationship between the opening area of the outer side port of FIG. 9 with respect to an outer side compression chamber, and the turning angle position of a turning scroll. In the first embodiment, the refrigerant supply amount (that is, the gas injection amount) supplied from both of the three virtual ports in FIG. It is. FIG. 2 is a cross-sectional view showing the III-III cross section of FIG. 2 in the second embodiment, showing the orbiting scroll at the suction completion position, and the port arrangement region and two virtual ports assumed as intermediate pressure ports. FIG. 10 is a diagram corresponding to FIG. 9 of the first embodiment. In the compressor of 2nd Embodiment, it is the operation | movement figure which each represented the relative positional relationship of the turning scroll with respect to a fixed scroll in the several turning angle position of a turning scroll, Comprising: It is a figure equivalent to FIG. 5 of 1st Embodiment. is there. In the cross-sectional view showing the III-III cross section of FIG. 2 in the second embodiment, the orbiting scroll is shown in the two-chamber combined position, and the port arrangement region and two virtual ports assumed as intermediate pressure ports are shown. FIG. It is the enlarged view which expanded and showed the XVI part of FIG. It is the enlarged view which expanded and showed the XVII part of FIG. In the compressor of 2nd Embodiment, it is the figure which showed the relationship between each of the volume of an inner side compression chamber, the volume of an outer side compression chamber, and those total volumes, and the turning angle position of a turning scroll, Comprising: It is a figure equivalent to FIG. 7 of a form. In the compressor of 2nd Embodiment, it is the figure which showed the relationship between each of the pressure of an inner side compression chamber, the pressure of an outer side compression chamber, and the pressure after combining of both compression chambers, and the turning angle position of a turning scroll. FIG. 9 is a diagram corresponding to FIG. 8 of the first embodiment. In 2nd Embodiment, it is the figure which showed the relationship between the opening area of the inner side port of FIG. 16 with respect to an inner side compression chamber, and the turning angle position of a turning scroll, Comprising: It is a figure equivalent to FIG. 11A of 1st Embodiment. is there. In 2nd Embodiment, it is the figure which showed the relationship between the opening area of the outer side port of FIG. 17 with respect to an outer side compression chamber, and the turning angle position of a turning scroll, Comprising: It is a figure equivalent to FIG. 11C of 1st Embodiment. is there. In 2nd Embodiment, it is the figure which showed the supply_amount | feed_rate of the refrigerant | coolant supplied from both of two virtual ports of FIG. 16 and FIG. FIG. 17 is an enlarged view illustrating an XVI portion of FIG. 13 in the third embodiment, and corresponds to FIG. 16 of the second embodiment. It is the figure which extracted and showed only the intermediate pressure port in the enlarged view which expanded and showed the XXIII part of FIG. It is sectional drawing which showed the XXIV-XXIV cross section of FIG. In 3rd Embodiment, it is the figure which showed the relationship between the opening area of the intermediate pressure port of FIG. 22 with respect to an inner side compression chamber, and the turning angle position of a turning scroll, Comprising: It is a figure equivalent to FIG. 20A of 2nd Embodiment. is there.

  Hereinafter, each embodiment will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
As shown in FIG. 1, the scroll compressor 1 (hereinafter simply referred to as the compressor 1) of the present embodiment constitutes a part of the refrigeration cycle 100. That is, the compressor 1 of the present embodiment sucks the refrigerant that is the fluid circulating in the refrigeration cycle 100, and compresses and discharges the sucked refrigerant.

Further, since the refrigeration cycle 100 of the present embodiment is configured as a two-stage compression cycle, a refrigerant having an intermediate pressure Pm is injected by the compressor 1. The refrigerant circulating in the refrigeration cycle 100 is, for example, carbon dioxide (that is, CO ₂ ). For example, the refrigeration cycle 100 in FIG. 1 forms part of a hot water supply system. 1 indicates the enthalpy of the refrigerant circulating in the refrigeration cycle 100, and the vertical axis indicates the pressure of the refrigerant. Further, “GI” in FIG. 1 is an abbreviation for gas injection.

  The refrigeration cycle 100 includes a radiator 2, a first expansion valve 3, an internal heat exchanger 4, a second expansion valve 5, and an evaporator 6, in addition to the compressor 1 that compresses and discharges the refrigerant that is the sucked fluid. And.

  High-pressure refrigerant discharged from the refrigerant discharge port 49 of the compressor 1 flows into the radiator 2. The radiator 2 performs heat exchange between the refrigerant flowing in and a fluid to be heated such as water or air, and radiates heat from the refrigerant by the heat exchange. The radiated refrigerant flows from the radiator 2 to each of the first expansion valve 3 and the high temperature side heat exchanging portion 4 a of the internal heat exchanger 4.

  The first expansion valve 3 decompresses the refrigerant that has flowed from the radiator 2 into the first expansion valve 3. The refrigerant pressure after depressurization in the first expansion valve 3 is the intermediate pressure Pm of the refrigerant in the refrigeration cycle 100 of FIG. The intermediate pressure Pm of the refrigerant is lower than the pressure of the high-pressure refrigerant discharged from the refrigerant discharge port 49 by the compressor 1 and higher than the pressure of the low-pressure refrigerant sucked by the compressor 1 through the refrigerant intake port 36. The refrigerant decompressed by the first expansion valve 3 flows from the first expansion valve 3 to the low temperature side heat exchange part 4b of the internal heat exchanger 4.

  The internal heat exchanger 4 includes a high temperature side heat exchange unit 4a and a low temperature side heat exchange unit 4b configured integrally with the high temperature side heat exchange unit 4a. Then, as indicated by arrow H1, the internal heat exchanger 4 heats the refrigerant flowing from the radiator 2 to the high temperature side heat exchange unit 4a and the refrigerant flowing from the first expansion valve 3 to the low temperature side heat exchange unit 4b. Exchange. The refrigerant flowing out from the high temperature side heat exchange unit 4a flows to the second expansion valve 5, and the refrigerant flowing out from the low temperature side heat exchange unit 4b flows to the intermediate pressure inlet 39 of the compressor 1.

  The second expansion valve 5 depressurizes the refrigerant that has flowed into the second expansion valve 5 from the high temperature side heat exchange part 4 a of the internal heat exchanger 4. At this time, the second expansion valve 5 depressurizes the refrigerant to a pressure lower than the refrigerant pressure after depressurization in the first expansion valve 3. The refrigerant flowing out from the second expansion valve 5 flows to the evaporator 6.

  The first expansion valve 3 and the second expansion valve 5 of the present embodiment are both electric expansion valves. For example, the valve opening degree of the first expansion valve 3 and the valve opening degree of the second expansion valve 5 are each adjusted according to a control signal from a control device (not shown).

  The evaporator 6 performs heat exchange between the refrigerant flowing in from the second expansion valve 5 and a fluid to be cooled such as water or air, and evaporates the refrigerant by the heat exchange. The refrigerant that has absorbed heat with the evaporation flows from the evaporator 6 to the refrigerant suction port 36 of the compressor 1, and is sucked into the compressor 1 through the refrigerant suction port 36.

  FIG. 2 is a cross-sectional view of the compressor 1 included in the refrigeration cycle 100 of FIG. An arrow DR1 in FIG. 2 indicates the vertical direction DR1 of the compressor 1. A compressor 1 shown in FIG. 2 is a scroll-type electric compressor, and a compression mechanism unit 10 that compresses refrigerant and an electric motor unit 20 that drives the compression mechanism unit 10 are arranged in a vertical direction (in other words, a vertical direction). It is a vertically placed type. The compressor 1 includes a compression mechanism unit 10, an electric motor unit 20, a housing 30, an oil separator 40, and the like.

  The housing 30 is an airtight container that forms an outer shell of the compressor 1 and is airtight. The housing 30 roughly has a cylindrical shape with both ends closed, and includes a cylindrical member 31 having the vertical direction DR1 as an axial direction, and a lid member 32 provided on the upper side of the cylindrical member 31. The bottom member 33 is provided below the cylindrical member 31. The housing 30 accommodates the compression mechanism unit 10 and the electric motor unit 20 in the housing 30.

  The electric motor unit 20 includes a stator 21 that forms a stator, and a rotor 22 that is disposed inside the stator 21 and forms a rotor. The stator 21 has a stator core and a stator coil wound around the stator core.

  A drive shaft 25 is inserted inside the rotor 22, and the drive shaft 25 is connected to the rotor 22 so as not to rotate relative to the rotor 22. Therefore, when the electric motor unit 20 is supplied with electric power through the power supply terminal 23, the electric motor unit 20 rotates the drive shaft 25 and the rotor 22 integrally around the compressor axis C1. The compressor axis C1 is a single axis C1 extending in the vertical direction DR1. That is, in the present embodiment, the axial direction DRa of the compressor shaft center C1 coincides with the vertical direction DR1. In the following description, the axial direction DRa of the compressor axis C1 is also referred to as a compressor axial direction DRa.

  The drive shaft 25 includes a rotor insertion shaft portion 251, a flange portion 252, and a lower end portion 253. The rotor insertion shaft portion 251, the flange portion 252 and the lower end portion 253 are integrated. The rotor insertion shaft portion 251 is a rotation shaft having the compressor shaft center C <b> 1 as a central axis, and is inserted inside the rotor 22. On the other hand, the flange portion 252 and the lower end portion 253 are provided below the rotor 22.

  The flange portion 252 of the drive shaft 25 is formed so as to protrude like a flange in the radial direction DRr of the compressor shaft center C1. Further, a balance weight 254 is provided on the collar portion 252.

  An upper end portion of the rotor insertion shaft portion 251 protrudes upward from the rotor 22 and is inserted into a bearing member 27 fixed to the housing 30. Further, the lower end portion of the rotor insertion shaft portion 251 connected to the flange portion 252 protrudes downward from the rotor 22 and is inserted into the bearing portion 291 of the middle housing 29 fixed to the housing 30. Thereby, the drive shaft 25 is supported so that it can rotate around the compressor axis C1.

  The compression mechanism unit 10 includes a turning scroll 11 and a fixed scroll 12. The orbiting scroll 11 is disposed below the middle housing 29, and the fixed scroll 12 is disposed below the orbiting scroll 11.

  The orbiting scroll 11 is a orbiting side member that orbits around the compressor axis C <b> 1 with respect to the fixed scroll 12. The fixed scroll 12 is a fixed side member as a non-rotating member fixed to the housing 30.

  As shown in FIGS. 2 and 3, the orbiting scroll 11 includes a disk-shaped orbiting base 111 and a swirl tooth 112 having a spiral shape. The turning tooth portion 112 is provided so as to protrude downward from the turning base portion 111 (that is, one side in the compressor axial direction DRa). The turning tooth portion 112 is also called a turning scroll wrap. In addition, in FIG. 3, the turning tooth part 112 and the fixed tooth part 122 are extracted and illustrated, and illustration of other parts is omitted. This method of illustration is the same in FIGS. 5, 9, 13 to 17, and 22 described later.

  The fixed scroll 12 has a disk-shaped fixed base part 121 and a fixed tooth part 122 having a spiral shape. The fixed base part 121 is arranged on the lower side with respect to the turning base part 111, and the fixed base part 121 and the turning base part 111 are arranged to face each other in the vertical direction DR1. The fixed tooth portion 122 is provided so as to protrude upward from the fixed base portion 121 (that is, the other side in the compressor axial direction DRa). The fixed tooth portion 122 is also called a fixed scroll wrap.

  A shaft insertion portion 113 is formed on the upper side of the swivel base 111 so as to protrude upward in a cylindrical shape. The shaft insertion portion 113 is disposed at the center portion of the turning base portion 111, and the lower end portion 253 of the drive shaft 25 is fitted into the shaft insertion portion 113. Further, the lower end portion 253 of the drive shaft 25 is an eccentric portion 253 that is eccentric with respect to the compressor shaft center C1.

  In addition, the compression mechanism unit 10 includes a rotation prevention mechanism (not shown) that prevents the turning scroll 11 from rotating. Therefore, the orbiting scroll 11 does not rotate and rotates with respect to the fixed scroll 12 along an annular locus centering on the compressor axis C1 as the drive shaft 25 rotates. In short, the orbiting scroll 11 revolves in a predetermined revolution direction DRrt with the compressor axis C1 as the revolution center.

  Since the fixed tooth portion 122 is formed in a spiral shape, the mutual gap between the fixed tooth portions 122 is a spiral fixed scroll groove 12a. And the fixed tooth part 122 and the turning tooth part 112 are mutually engaged so that the turning tooth part 112 may be inserted in the fixed scroll groove | channel 12a. In other words, the teeth 112 and 122 mesh with each other.

  Further, the swivel tooth portion 112 has an inward side surface 112 a facing the inner peripheral side of the swivel tooth portion 112 and an outward side surface 112 b facing the outer peripheral side of the swivel tooth portion 112 as side wall surfaces of the swivel tooth portion 112. Yes. Similarly, the fixed tooth portion 122 has an inward side surface 122 a facing the inner peripheral side of the fixed tooth portion 122 and an outward side surface 122 b facing the outer peripheral side of the fixed tooth portion 122 as side wall surfaces of the fixed tooth portion 122. ing. Both of the side wall surfaces 112a and 112b of the swivel tooth portion 112 and both of the side wall surfaces 122a and 122b of the fixed tooth portion 122 are configured by involute curves.

  Note that the compressor 1 of the present embodiment is a symmetrical scroll in which the winding end angle of the swivel tooth portion 112 and the winding end angle of the fixed tooth portion 122 are equal or substantially equal. The number of turns of the swivel tooth portion 112 and the fixed tooth portion 122 is two. However, the shape of the winding tooth portion 112 at the start of winding (in other words, the shape of the inner peripheral end of the spiral) is different from the shape of the winding start of the fixed tooth portion 122.

  As shown in FIGS. 3 and 4, the fixed base portion 121 has a fixed base surface 121 a formed between the spiral fixed tooth portions 122. And the fixed tooth part 122 protrudes upwards with respect to the fixed base surface 121a. The fixed base surface 121a is an upward surface and faces the tip surface 112c of the swivel tooth portion 112.

  The fixed tooth portion 122 has a base end 122c located at the boundary with the fixed base surface 121a. And the base end 122c of the fixed tooth part 122 has the base end inner side edge 122d on the radial inner side of the base end 122c, and has the base end outer side edge 122e on the radial outer side of the base end 122c. . As described above, since both the side wall surfaces 122a and 122b of the fixed tooth portion 122 are each configured by an involute curve, the proximal end inner side edge 122d and the proximal end outer side edge 122e are also configured by an involute curve. .

  The tip surface 112 c of the swivel tooth portion 112 is a downward surface and is formed at the tip of the swivel tooth portion 112. The tip surface 112c has a tip surface inner side edge 112d on the radially inner side of the tip surface 112c. At the same time, the tip surface 112c has a tip surface outer side edge 112e on the radially outer side of the tip surface 112c. As described above, since both the side wall surfaces 112a and 112b of the swivel tooth portion 112 are each configured by an involute curve, the tip surface inner side edge 112d and the tip surface outer side edge 112e are each configured by an involute curve.

  The swivel tooth portion 112 and the fixed base portion 121 form an inner compression chamber 10a and an outer compression chamber 10b for compressing the refrigerant flowing from the refrigerant suction port 36 between the swivel tooth portion 112 and the fixed base portion 121, respectively. ing. The inner compression chamber 10 a is located on the radially inner side of the swivel tooth portion 112 and is formed so as to be sandwiched between the inward side surface 112 a of the swivel tooth portion 112 and the outward side surface 122 b of the fixed tooth portion 122. Further, the outer compression chamber 10 b is located on the radially outer side of the swivel tooth portion 112 and is formed so as to be sandwiched between the outward side surface 112 b of the swivel tooth portion 112 and the inward side surface 122 a of the fixed tooth portion 122.

  That is, a part of the fixed scroll groove 12a formed in the fixed scroll 12 is the compression chambers 10a and 10b. Specifically, the tooth portions 112 and 122 of the scrolls 11 and 12 mesh with each other and contact at a plurality of locations, thereby forming an inner compression chamber 10a and an outer compression chamber 10b. The inner compression chamber 10a is also called an inner working chamber, and the outer compression chamber 10b is also called an outer working chamber.

  As shown in FIGS. 3 and 5, the orbiting scroll 11 orbits in the direction of the arrow DRrt. The orbiting scroll 11 moves the inner compression chamber 10a and the outer compression chamber 10b radially inward along with the orbiting movement of the orbiting scroll 11, and the volume of the inner compression chamber 10a and the volume of the outer compression chamber 10b. Decrease.

  5A to 5H each show a cross section of the compression mechanism unit 10 at each turning angle position in the turning movement of the turning scroll 11. The turning angle position of the orbiting scroll 11 is also the rotational position of the drive shaft 25 (see FIG. 2) that orbits the orbiting scroll 11.

  Specifically, in FIGS. 5A to 5H, the turning angle position at which the orbiting scroll 11 completes the inflow of the refrigerant from the refrigerant suction port 36 to the compression chambers 10a and 10b is the 0 deg position and the revolution direction DRrt ( 3) is shown as the positive direction of the turning angle position. Accordingly, FIG. 5A shows a cross section when the turning angle position of the orbiting scroll 11 is the 0 deg position, and FIG. 5B shows a cross section when the turning angle position is the 45 deg position. 5 (c) shows a cross section when the turning angle position is a 90 deg position. 5D shows a cross section when the turning angle position is a 135 deg position, FIG. 5E shows a cross section when the turning angle position is a 180 deg position, and FIG. ) Shows a cross section when the turning angle position is a 225 deg position. Further, FIG. 5G shows a cross section when the turning angle position is 270 deg position, and FIG. 5H shows a cross section when the turning angle position is 315 deg position.

  5A to 5H, the discharge port 123 is not shown, and this is the same in FIGS. 14A to 14H described later. Further, FIG. 5A is a cross section at the 0 deg position as described above, but is also a cross section at the 360 deg position. Further, since the turning angle position of the orbiting scroll 11 shown in FIG. 3 and FIG. 9 described later is the 0 deg position, the relative positional relationship between the orbiting tooth portion 112 and the fixed tooth portion 122 in FIG. 3 and FIG. This is the same as FIG.

  As shown in FIGS. 2 and 3, the compression mechanism unit 10 includes a supply unit 14 that supplies a refrigerant to the inner compression chamber 10 a and the outer compression chamber 10 b. A refrigerant supply chamber is formed inside the supply unit 14, and the low-pressure refrigerant flowing out of the evaporator 6 (see FIG. 1) is supplied to the supply unit 14 via the refrigerant suction port 36 as indicated by an arrow FLin. Inflow. The supply part 14 is arrange | positioned so that a low pressure refrigerant | coolant can be supplied to each of the inner side compression chamber 10a and the outer side compression chamber 10b from the outer peripheral side of the turning tooth part 112 or the outer peripheral side of the fixed tooth part 122. That is, the supply unit 14 communicates with the outermost peripheral portion of the fixed scroll groove 12a.

  A discharge port 123 through which the refrigerant compressed in both the compression chambers 10a and 10b is discharged is formed on the fixed base surface 121a. The refrigerant compressed in both the compression chambers 10a and 10b is discharged from the discharge port 123 after the two compression chambers 10a and 10b communicate with each other. The discharge port 123 is a circular hole opened in the fixed base surface 121a, and is closed by being covered with the tip surface 112c of the swivel tooth portion 112, for example, as shown in FIGS. Note that the compression chambers 10a and 10b communicate with each other and will be described later.

  As shown in FIGS. 2 and 3, the fixed base 121 has a discharge chamber 124 in addition to the discharge port 123. The discharge port 123 communicates with the discharge chamber 124 on the side opposite to the fixed scroll groove 12a side. A check valve 19 is provided in the discharge chamber 124, and the check valve 19 allows the refrigerant to flow from the discharge port 123 into the discharge chamber 124, while at the same time from the discharge chamber 124 to the discharge port 123. Prevents the outflow of refrigerant.

  The discharge chamber 124 is connected to the refrigerant discharge port 49 of the compressor 1 through the discharge refrigerant pipe 48 and the oil separator 40 in order. Accordingly, the refrigerant in the discharge chamber 124 flows into the oil separator 40 via the discharge refrigerant pipe 48 and is separated from the lubricating oil in the oil separator 40. Then, the separated refrigerant is discharged from the refrigerant discharge port 49 to the radiator 2 (see FIG. 1) as indicated by an arrow FLout. The refrigerant discharge port 49 of the compressor 1 is also a refrigerant outlet 49 of the oil separator 40.

  The oil separator 40 has an oil reservoir tank 401. The lubricating oil separated from the refrigerant in the oil separator 40 is temporarily stored in the oil reservoir tank 401, and returned from the oil reservoir tank 401 to the housing 30 through the oil feed pipe 41. In addition, an oil storage chamber 35 in which lubricating oil is accumulated is formed at the bottom of the housing 30.

  Next, an injection device that joins the refrigerant having the intermediate pressure Pm supplied from the low temperature side heat exchange section 4b of the internal heat exchanger 4 of FIG. 1 to the intermediate pressure inlet 39 of the compressor 1 to the refrigerant being compressed will be described. .

  As shown in FIGS. 2 and 3, the compression mechanism unit 10 has a check valve 50 embedded in the fixed base 121 from below. Further, an intermediate pressure port 125 as a gas injection port 125 is formed on the fixed base surface 121a. In the present embodiment, the intermediate pressure port 125 is provided at one place on the fixed base surface 121a. For example, the intermediate pressure port 125 is configured as one communication hole.

  The intermediate pressure port 125 is a circular hole opened in the fixed base surface 121a. That is, one end of a circular hole serving as the intermediate pressure port 125 is connected to the fixed scroll groove 12 a, and the other end of the circular hole is connected to the check valve 50.

  As shown in FIGS. 3 and 6, the intermediate pressure port 125 is closed when the opening end 125 a serving as the one end of the intermediate pressure port 125 is covered with the distal end surface 112 c of the turning tooth portion 112.

  Specifically, the intermediate pressure port 125 is opened and closed by the turning tooth portion 112 as the turning scroll 11 turns. In the present embodiment, the intermediate pressure port 125 communicates with the inner compression chamber 10a every rotation of the orbiting scroll 11, and the refrigerant in the middle of compression in the communicated inner compression chamber 10a is transferred to the outside of the compressor 1 ( Specifically, the refrigerant from the low temperature side heat exchange section 4b) in FIG.

  Further, the intermediate pressure port 125 has at least a part of the intermediate pressure port 125 between the inner peripheral end and the outer peripheral end of the fixed base surface 121a along the spiral shape of the fixed tooth portion 122. It arrange | positions so that it may open. In the present embodiment, the portion of the fixed base 121 where the intermediate pressure port 125 is formed and the check valve 50 constitute the injection device.

  Further, as shown in FIG. 2, the intermediate pressure port 125 is connected to the intermediate pressure suction port 39 (see FIG. 2) through the check valve 50 and the intermediate pressure introduction passage 51 provided below the check valve 50 in this order. 1). The check valve 50 allows the refrigerant flow from the intermediate pressure inlet 39 to the intermediate pressure port 125, while allowing the refrigerant flow from the intermediate pressure port 125 to the intermediate pressure inlet 39 (that is, the refrigerant reverse flow). Stop.

  In the compressor 1 of the present embodiment configured as described above, the volume Vi of the inner compression chamber 10a, the volume Vo of the outer compression chamber 10b, and the total volume Vio of the inner compression chamber 10a and the outer compression chamber 10b are shown in FIG. As shown in FIG.

  Here, in FIG. 7, the vertical axis indicates the compression chamber volumes Vi, Vo, and Vio, and the horizontal axis indicates the turning angle position of the orbiting scroll 11. The 0 deg position and the positive direction of the turning angle position of the turning scroll 11 indicated by the horizontal axis in FIG. 7 are the same as the turning angle position of the turning scroll 11 shown in FIG. Therefore, at the 0 deg position of the orbiting scroll 11 shown in FIG. 7, the compression chambers 10a and 10b are formed as shown in FIG. 5A, and the inflow of the refrigerant into the compression chambers 10a and 10b is completed. Strictly speaking, the refrigerant is sucked into the compression chambers 10a and 10b until just before the 0 deg position of the orbiting scroll 11, and the refrigerant suction into the compression chambers 10a and 10b is finished at the 0 deg position.

  That is, when the orbiting scroll 11 shown in FIG. 5 (a) reaches the 0 deg position, the communication between the inner compression chamber 10a and the supply unit 14 is cut off, so that the supply unit 14 moves to the inner compression chamber 10a. Is the time when the inflow of the refrigerant is completed, that is, the time when the suction of the inner compression chamber 10a is completed. Then, when the 0 deg position is reached, the communication between the outer compression chamber 10b and the supply unit 14 is cut off, whereby the refrigerant flow from the supply unit 14 to the outer compression chamber 10b is completed, that is, the outer side. It is also the time when the suction of the compression chamber 10b is completed. The compression period in which the refrigerant is compressed in the inner compression chamber 10a starts from the completion of the suction of the inner compression chamber 10a, and the compression period in which the refrigerant is compressed in the outer compression chamber 10b is the completion of the suction of the outer compression chamber 10b. Therefore, both compression periods start at the same time.

  In other words, the orbiting scroll 11 blocks communication between the outer compression chamber 10b and the supply unit 14 when the orbiting angular position of the orbiting scroll 11 reaches a predetermined outer suction completion position R1. The inflow of the refrigerant from the supply unit 14 to the outer compression chamber 10b is completed. At the same time, the orbiting scroll 11 disconnects the communication between the inner compression chamber 10a and the supply unit 14 from the supply unit 14 when the orbiting angular position reaches a predetermined inner suction completion position R2. The inflow of the refrigerant to 10a is completed. Further, since the compressor 1 is a symmetric scroll compressor, the orbiting scroll 11 pivots so as to reach the inner suction completion position R2 at the same timing as it reaches the outer suction completion position R1. In short, the suction completion positions R1 and R2 are both 0 deg positions and are the same as each other.

  Moreover, the compressor 1 of this embodiment continues refrigerant | coolant compression in each compression chamber 10a, 10b, even if the turning scroll 11 exceeds a 360deg position. Then, from the 360 deg position of the orbiting scroll 11 shown in FIG. 7, as shown in FIG. 5A, the orbiting scroll 11 starts to communicate the inner compression chamber 10a and the outer compression chamber 10b with each other. That is, during the compression period of the inner compression chamber 10a and the outer compression chamber 10b, the inner compression chamber 10a and the outer compression chamber 10b begin to communicate with each other.

  In other words, the orbiting scroll 11 starts communicating the inner compression chamber 10a and the outer compression chamber 10b with each other when the orbiting angular position of the orbiting scroll 11 reaches the predetermined two-chamber combined position R3. And since both the number of turns of the turning tooth part 112 and the fixed tooth part 122 is 2, the two-chamber combined position R3 is a 360 deg position. Strictly speaking, the two compression chambers 10a and 10b are not yet communicated with each other at the two-chamber combined position R3, and the two compression chambers 10a and 10b begin to communicate with each other immediately after the two-chamber combined position.

  As shown in FIG. 7, the inner compression chamber volume Vi, which is the volume Vi of the inner compression chamber 10a, smoothly decreases from the 0 deg position to the 360 deg position of the orbiting scroll 11. On the other hand, the outer compression chamber volume Vo, which is the volume Vo of the outer compression chamber 10b, rapidly decreases from the vicinity where the orbiting scroll 11 exceeds the 200 deg position. This is because the shape of the inward side surface 122a of the fixed tooth portion 122 facing the outer compression chamber 10b is surrounded by a two-dot chain line D1 in FIG. Because it contains. This is because the outer compression chamber 10b reaches the arc-shaped portion of the inward side surface 122a.

  In short, in the compressor 1 of this embodiment, as can be seen from FIG. 7, if the volume changes of both the compression chambers 10 a and 10 b are compared with each other, the inner compression chamber 10 a The volume changes more slowly than the chamber 10b. That the volume change is gradual means that, in other words, in the orbiting movement of the orbiting scroll 11, the rate of decrease in the volume of the compression chambers 10a and 10b with respect to the amount of change in the orbiting angular position of the orbiting scroll 11 is small.

  From the changes in the compression chamber volumes Vi, Vo, and Vio shown in FIG. 7, the pressure Pi of the inner compression chamber 10a, the pressure Po of the outer compression chamber 10b, and the pressure Pio after combining the inner compression chamber 10a and the outer compression chamber 10b. As shown in FIG. 8, each of them changes as the orbiting scroll 11 turns. 8 indicates the compression chamber pressures Pi, Po, and Pio, and the horizontal axis in FIG. 8 indicates the same turning angle position of the orbiting scroll 11 as in FIG. 8 indicates the turning angle position of the orbiting scroll 11 at which the discharge port 123 starts to open. Further, the compression chamber pressures Pi, Po, Pio are the pressures of the refrigerant in the compression chambers 10a, 10b in detail.

  Specifically, as shown in FIG. 8, the inner compression chamber pressure Pi, which is the pressure Pi of the inner compression chamber 10a, smoothly rises from the 0 deg position to the 360 deg position of the orbiting scroll 11. On the other hand, the outer compression chamber pressure Po, which is the pressure Po of the outer compression chamber 10b, rapidly increases from around the turning scroll 11 beyond the 200 deg position. That the change in the pressure Po is abrupt means, in other words, that the rate of increase of the pressure Po with respect to the amount of change in the turning angle position of the turning scroll 11 is large in the turning movement of the turning scroll 11.

  Further, the compression completion time point when the orbiting scroll 11 reaches the compression completion position Rop where the discharge port 123 starts to open with respect to both the compression chambers 10a and 10b is after the two-chamber combination time point when the orbiting scroll 11 reaches the two-chamber combination position R3. It is. Therefore, the compression period of the inner compression chamber 10a and the compression period of the outer compression chamber 10b end at the same compression completion point.

  Next, the range in which the intermediate pressure port 125 can be arranged in the fixed base surface 121a will be described. As shown in FIGS. 2 and 3, the intermediate pressure port 125 is arranged so as to satisfy all of the first to third conditions described below in order not to impair the efficiency of the compressor 1. There is a need. The first condition is that the intermediate pressure port 125 does not communicate with the supply unit 14 via the inner compression chamber 10a or the outer compression chamber 10b. The second condition is that the intermediate pressure port 125 communicates with the inner compression chamber 10a or the outer compression chamber 10b until the inner compression chamber 10a and the outer compression chamber 10b are joined (in other words, communicated) with each other. The opening period is complete. The third condition is that the inner compression chamber 10 a and the outer compression chamber 10 b do not communicate with each other via the intermediate pressure port 125. For example, if the diameter of the intermediate pressure port 125 is larger than the thickness of the swivel tooth portion 112, the inner compression chamber 10a and the outer compression chamber 10b can communicate with each other via the intermediate pressure port 125, so the third condition is satisfied. In order to do that, it is necessary not to be.

  Specifically, the port arrangement region Ap of the intermediate pressure port 125 that satisfies all the above first to third conditions is a hatched region that intersects with each other in FIG. 9 in the fixed base surface 121a. . That is, the range in which the intermediate pressure port 125 can be arranged is the port arrangement region Ap. If the intermediate pressure port 125 does not protrude from the port arrangement area Ap and opens so as to be within the port arrangement area Ap, all of the first to third conditions are satisfied. In the present embodiment, the intermediate pressure port 125 does not protrude from the port arrangement area Ap, and is open so as to be within the port arrangement area Ap.

  Specifically, in the compressor 1 of the present embodiment, the port arrangement region Ap is a single closed region provided on the fixed base surface 121a and extending in the spiral direction DRg of the fixed tooth portion 122, as shown in FIG. Composed. Note that the spiral direction DRg of the fixed tooth portion 122 is a direction along the spiral shape of the fixed tooth portion 122. The peripheral edge ALp of the port arrangement region Ap is composed of a first curve L1, a second curve L2, a third curve L3, a fourth curve L4, a fifth curve L5, and a sixth curve L6.

  And the 1st curve L1 is a curve which comprises a part of front end surface outer side edge 112e of the turning scroll 11 in the outer side suction completion position R1. The second curve L2 is a curve constituting a part of the front end surface inner side edge 112d of the orbiting scroll 11 at the two-chamber combined position R3. The third curve L3 is a curve that is spaced by the thickness TKr of the swiveling tooth portion 112 while maintaining an equal interval to the proximal inner side edge 122d radially inward of the fixed scroll 12 (that is, offset by the thickness TKr). Curve) constituting a part of the curve. The fourth curve L4 is a curve that is spaced apart by the thickness TKr of the swiveling tooth portion 112 while maintaining an equal interval to the radially outer side of the fixed scroll 12 with respect to the proximal outer side edge 122e (that is, offset by the thickness TKr). Curve) constituting a part of the curve. The fifth curve L5 is a curve that constitutes a part of the outer edge 112e on the front end surface of the orbiting scroll 11 at the two-chamber merge position R3. The sixth curve L6 is a curve that constitutes a part of the leading end inner side edge 112d of the orbiting scroll 11 at the inner suction completion position R2.

  Here, since the compressor 1 of this embodiment is a symmetrical scroll compressor in which the number of turns of the tooth portions 112 and 122 of the scrolls 11 and 12 is two, the fifth curve L5 is the first curve L1. And the sixth curve L6 matches the second curve L2. Therefore, in FIG. 9, the peripheral edge ALp of the port arrangement area Ap apparently includes a first curve L1, a second curve L2, a third curve L3, and a fourth curve L4.

  Note that although the third curve L3 is equally spaced with respect to the proximal inner side edge 122d, the radius of curvature of the third curve L3 is the third curved line L3 of the proximal inner side edge 122d. In contrast, the radius of curvature of the portions adjacent to each other in parallel is smaller by the thickness TKr of the turning tooth portion 112. Further, since the fourth curve L4 is equally spaced with respect to the base end outer side edge 122e, the curvature radius of the fourth curve L4 is adjacent to the fourth curve L4 in the base end outer side edge 122e in parallel. The radius of curvature of the portion is larger by the thickness TKr of the swivel tooth portion 112.

  The range in which the intermediate pressure port 125 can be arranged is as described above, but in order to increase the efficiency of the compressor 1, the total suction amount from the intermediate pressure port 125 to both the compression chambers 10a and 10b should be increased. . Then, next, it is preferable to arrange the intermediate pressure port 125 in the port arrangement region Ap of FIG. 9 in order to increase the total suction amount.

  In the following description, as shown in FIG. 9, which of the virtual inner side port 126a, the central port 126b, and the outer side port 126c should be selected as the intermediate pressure port 125 will be considered. These three virtual ports 126a, 126b, and 126c are candidates for the intermediate pressure port 125, respectively. Further, all of the three virtual ports 126a, 126b, and 126c are circular holes having the same hole diameter.

  As shown in FIG. 9, the inward port 126a has a fixed tooth portion within the maximum inscribed circle range in which the inscribed circle inscribed in the peripheral edge ALp of the port arranged region Ap is the largest in the port arranged region Ap. 122 is arranged on the outermost peripheral side in the spiral direction DRg. In other words, the inner-side port 126a is disposed at a position farthest from the discharge port 123 along the spiral shape of the fixed tooth portion 122 within the maximum inscribed circle range. Then, as shown in FIG. 10, the inward port 126 a is arranged so as to be biased inward in the radial direction DRb of the fixed scroll 12 among the surface width Wf of the fixed base surface 121 a corresponding to the mutual interval between the fixed tooth portions 122. Has been.

  Further, as shown in FIGS. 9 and 10, the center port 126b is arranged in the maximum inscribed circle range in the port arrangement area Ap, and is arranged in the center of the surface width Wf of the fixed base surface 121a. Yes.

  Further, as shown in FIG. 9, the outer side port 126c is arranged on the innermost peripheral side in the spiral direction DRg of the fixed tooth portion 122 in the maximum inscribed circle range in the port arrangement region Ap. In other words, the outer side port 126c is disposed at a position closest to the discharge port 123 along the spiral shape of the fixed tooth portion 122 in the maximum inscribed circle range. And as shown in FIG. 10, the outer side port 126c is arrange | positioned so that it may be biased outside in the radial direction DRb of the fixed scroll 12 in the surface width Wf of the fixed base surface 121a.

  A solid line Lim in FIG. 11A represents a change in the opening area of the inner side port 126a with respect to the inner compression chamber 10a. As shown in FIG. 11A, the inner-side port 126a opens to the inner compression chamber 10a, but does not open to the outer compression chamber 10b. 11A to 11C, the horizontal axis indicates the turning angle position of the orbiting scroll 11, and the vertical axis indicates the opening area of the virtual ports 126a, 126b, and 126c with respect to the compression chambers 10a and 10b.

  Moreover, FIG. 11B represents the change of the opening area of the center port 126b with respect to each of the inner side compression chamber 10a and the outer side compression chamber 10b. That is, in FIG. 11B, a broken line Lom represents a change in the opening area of the central port 126b with respect to the outer compression chamber 10b, and a solid line Lim represents a change in the opening area of the central port 126b with respect to the inner compression chamber 10a. As shown in FIG. 11B, the center port 126b opens alternately to the inner compression chamber 10a and the outer compression chamber 10b.

  A broken line Lom in FIG. 11C represents a change in the opening area of the outer side port 126c with respect to the outer compression chamber 10b. As shown in FIG. 11C, the outer side port 126c opens to the outer compression chamber 10b, but does not open to the inner compression chamber 10a.

  As can be seen from FIGS. 11A to 11C, if the intermediate pressure port 125 is arranged at the position of the central port 126 b, the intermediate pressure port 125 opens to the inner compression chamber 10 a as the orbiting scroll 11 turns. The period and the opening period that opens to the outer compression chamber 10b have the same or substantially the same length.

  Then, as the arrangement of the intermediate pressure port 125 approaches the position of the inner port 126a from the position of the central port 126b in the port arrangement region Ap, the opening period for the outer compression chamber 10b becomes shorter and the opening period for the inner compression chamber 10a. Becomes longer. Conversely, the closer the position of the intermediate pressure port 125 is to the position of the outer port 126c from the position of the central port 126b in the port arrangement region Ap, the shorter the opening period for the inner compression chamber 10a and the opening for the outer compression chamber 10b. The period becomes longer.

  FIG. 12 shows the amount of refrigerant supplied from each of the three virtual ports 126a, 126b, 126c to the compression chambers 10a, 10b (that is, the amount of gas injection), and the amount of refrigerant supplied from the inner port 126a is 1. As shown. In FIG. 12, (i) the refrigerant supply amount from the inner port 126a, (ii) the refrigerant supply amount from the center port 126b, and (iii) the refrigerant supply amount from the outer port 126c are displayed in order from the left side. Yes. As will be described for confirmation, since the refrigerant is supplied from the central port 126b to each of the inner compression chamber 10a and the outer compression chamber 10b, the amount of gas injection from the central port 126b shown in FIG. This is the total amount of gas injection into 10a and 10b.

  As can be seen from FIG. 12, the gas injection amount from the inner side port 126a is the largest, and then the gas injection amount from the outer side port 126c is the largest. And the amount of gas injection from the central port 126b is the smallest.

  Therefore, in order to increase the gas injection amount, it is most preferable to arrange the intermediate pressure port 125 at the position of the inner side port 126a. Even if the intermediate pressure port 125 cannot be disposed at the position of the inner side port 126a for reasons such as the structure of the compressor 1, it is preferable that the intermediate pressure port 125 be disposed as close to the position of the inner side port 126a as possible.

  Here, the injection of the refrigerant from the intermediate pressure port 125 performed for the communication compression chamber of both the compression chambers 10a and 10b is an intermediate pressure Pm of the refrigerant flowing out from the low temperature side heat exchange section 4b in FIG. This is performed by a pressure difference between the refrigerant pressure in the communication compression chamber. The communication compression chamber is a compression chamber that communicates with the intermediate pressure port 125 as the orbiting scroll 11 turns in the compression chambers 10a and 10b.

  Since the refrigerant is injected by the pressure difference as described above, the refrigerant pressure in the communication compression chamber increases as the refrigerant is compressed in the communication compression chamber, and if the pressure becomes higher than the intermediate pressure Pm, the intermediate pressure is increased. The refrigerant cannot be injected from the port 125. During the period when the refrigerant pressure in the communication compression chamber is higher than the intermediate pressure Pm, the check valve 50 in FIG. 2 prevents the refrigerant from flowing back. As will be described later, the intermediate pressure port 125 communicates with the inner compression chamber 10a as the orbiting scroll 11 turns, but does not communicate with the outer compression chamber 10b. Therefore, the inner compression chamber 10a corresponds to the communication compression chamber. However, the outer compression chamber 10b does not correspond to the communication compression chamber.

  According to FIG. 8, the pressure increase in the outer compression chamber 10b is abrupt compared to the inner compression chamber 10a, so the pressure Po in the outer compression chamber 10b is earlier than the pressure Pi in the inner compression chamber 10a. The refrigerant reaches an intermediate pressure Pm. Therefore, the outer supply possible period PDo in which the refrigerant can be supplied from the intermediate pressure port 125 to the outer compression chamber 10b is the inner supply possible period PDi in which the refrigerant can be supplied from the intermediate pressure port 125 to the inner compression chamber 10a. Shorter than.

  Also from the difference between the outer supplyable period PDo and the inner supplyable period PDi shown in FIG. 8, the amount of gas injection from the inner side port 126a that opens exclusively to the inner compression chamber 10a is greater than the outer side port 126c. It turns out that it becomes large compared with the amount of gas injection.

  From the above examination results, in this embodiment, as shown in FIGS. 3, 6, and 9, the intermediate pressure port 125 has the opening end 125 a of the intermediate pressure port 125 within the port arrangement region Ap. Is arranged. Thus, the intermediate pressure port 125 does not communicate with the inner compression chamber 10a and the outer compression chamber 10b at the same time.

  The intermediate pressure port 125 is arranged at a position closer to the inner side port 126a between the position of the inner side port 126a and the position of the central port 126b in the port arrangement region Ap. Accordingly, the intermediate pressure port 125 is disposed on the inner side in the radial direction DRb of the fixed scroll 12 in the surface width Wf of the fixed base surface 121a. That is, the intermediate pressure port 125 arranged in the inner side as described above has a longer time in the inner compression chamber 10a than the outer compression chamber 10b in the fixed base surface 121a, as can be seen by comparing FIGS. 11A to 11C. It can be said that it is arranged at a site that communicates.

  In the present embodiment, the intermediate pressure port 125 communicates with the inner compression chamber 10a as the orbiting scroll 11 turns, but does not communicate with the outer compression chamber 10b. Further, in the present embodiment, since all of the first to third conditions described above are satisfied, the intermediate pressure port 125 is subjected to inner compression after the completion of suction of the inner compression chamber 10a during the compression period of the inner compression chamber 10a. Communication with the chamber 10a begins. Further, during the compression period, the communication between the intermediate pressure port 125 and the inner compression chamber 10a is blocked until the inner compression chamber 10a and the outer compression chamber 10b begin to communicate with each other.

  As described above, according to the present embodiment, as shown in FIGS. 3, 7, and 8, the inner compression chamber 10 a has a volume more gently than the outer compression chamber 10 b as the orbiting scroll 11 moves. Change. That is, the amount of change in the turning angle position of the orbiting scroll 11 from the suction completion positions R1 and R2 until the inner compression chamber pressure Pi reaches the intermediate pressure Pm in the orbiting movement of the orbiting scroll 11 is determined by the outer compression chamber pressure Po being the intermediate pressure. It is larger than the amount of change of the turning angle position of the turning scroll 11 until reaching Pm. And the intermediate pressure port 125 is arrange | positioned among the fixed base | substrate surfaces 121a in the site | part connected to the inner side compression chamber 10a for a long time rather than the outer side compression chamber 10b.

  Therefore, conversely, compared to the case where the intermediate pressure port 125 is disposed in a portion of the fixed base surface 121a that is in communication with the outer compression chamber 10b for a longer time than the inner compression chamber 10a, the intermediate pressure port 125 is not compressed. The total period of opening to each of 10b can be made longer. Therefore, it is possible to reduce the number of installation locations of the intermediate pressure port 125 while suppressing a decrease in the total amount of refrigerant supplied from the intermediate pressure port 125 to the inner compression chamber 10a and the outer compression chamber 10b. For example, it is possible to set the intermediate pressure port 125 to one place as in this embodiment while suppressing a decrease in the total supply amount of the refrigerant. In other words, a larger amount of gas injection can be secured, and the high capacity of the compressor 1 can be secured.

  Here, the compressor 1 of the present embodiment is a symmetric scroll compressor. In general, the symmetric scroll is an extension angle of each involute curve for forming the swivel tooth portion 112 and the fixed tooth portion 122. Are equal at the end of the outer winding. On the other hand, some symmetric scrolls are asymmetric with respect to the winding start at the center of the revolving tooth portion 112 and the fixed tooth portion 122 due to structural reasons such as the arrangement of the discharge port 123. For example, this is the compressor 1 of the present embodiment.

  In the symmetrical scroll compressor in which the winding start is asymmetric, the volume change of the inner compression chamber 10a and the volume change of the outer compression chamber 10b as the compression proceeds from the completion of the suction into the compression chambers 10a and 10b. Are different from each other. In such a compressor, for example, when the volume change of the outer compression chamber 10b is abrupt as shown in FIG. 7, the intermediate pressure port 125 is connected to the surface width Wf of the fixed base surface 121a as in this embodiment. Among them, it is preferable to arrange the fixed scroll 12 on the inner side in the radial direction DRb. If the intermediate pressure port 125 is arranged in this way, it is possible to ensure a long opening period of the intermediate pressure port 125 with respect to the inner compression chamber 10a. And, as the pressure Pi of the inner compression chamber 10a rises moderately as shown in FIG. 8, the pressure difference between the pressure Pi of the inner compression chamber 10a and the intermediate pressure of the gas injection can be secured, and a larger amount of gas injection can be achieved. It is possible to secure.

  Further, according to the present embodiment, as shown in FIG. 3, the intermediate pressure port 125 is provided at one place on the fixed base surface 121a. Therefore, compared with the case where the intermediate pressure port 125 is provided at a plurality of locations, the mechanical structure including the check valve 50 and the intermediate pressure introduction passage 51, that is, the mechanical structure related to the intermediate pressure port 125 is simplified. Can be achieved. In short, it is possible to simplify the injection apparatus.

  Further, according to the present embodiment, the intermediate pressure port 125 shown in FIG. 3 starts to communicate with the inner compression chamber 10a after the completion of the suction during the compression period of the inner compression chamber 10a as the communication compression chamber. During the compression period, the communication between the intermediate pressure port 125 and the inner compression chamber 10a is blocked until the inner compression chamber 10a and the outer compression chamber 10b begin to communicate with each other. Therefore, it is possible to reduce waste in the refrigerant supply from the intermediate pressure port 125. The waste refers to, for example, that the refrigerant from the intermediate pressure port 125 flows to the supply unit 14 in FIG. 2 or the pressure increase in one of the inner compression chamber 10a and the outer compression chamber 10b. Is a hindrance.

  Further, according to the present embodiment, as shown in FIGS. 3 and 9, the intermediate pressure port 125 is opened so as to be accommodated in the port arrangement region Ap configured by one closed region of the fixed base surface 121a. doing. Then, the peripheral edge ALp of the port arrangement region Ap has the first curve L1, the second curve L2, the third curve L3, the fourth curve L4, the fifth curve L5, and the sixth curve L6 described above with reference to FIG. Have. Therefore, by opening the intermediate pressure port 125 so as to be within the port arrangement region Ap of FIG. 9, it is possible to reduce waste in the refrigerant supply from the intermediate pressure port 125 described above.

  Further, according to the present embodiment, as shown in FIGS. 3 and 5, the orbiting scroll 11 orbits so as to reach the inner suction completion position R2 at the same timing as it reaches the outer suction completion position R1. . Therefore, in the compressor 1 that is a symmetrical scroll, it is possible to reduce the number of installation locations of the intermediate pressure port 125 while suppressing a decrease in the total supply amount of the refrigerant.

  Further, according to the present embodiment, as shown in FIGS. 3 and 9, the port arrangement region Ap is one closed region extending in the spiral direction DRg along the spiral shape of the fixed tooth portion 122. And the intermediate pressure port 125 is arrange | positioned in the position close | similar to the one side of the spiral direction DRg of the fixed tooth part 122 among port arrangement | positioning area | region Ap. In short, the intermediate pressure port 125 is not arranged in the center of the spiral direction DRg in the port arrangement region Ap.

  Therefore, compared with the case where the intermediate pressure port 125 is arranged in the center of the spiral direction DRg of the fixed tooth portion 122 in the port arrangement region Ap, as shown in FIG. 12, the refrigerant supply amount from the intermediate pressure port 125, that is, It is possible to increase the gas injection amount.

  Further, according to the present embodiment, as shown in FIGS. 3 and 6, the intermediate pressure port 125 communicates with the inner compression chamber 10 a as the orbiting scroll 11 moves, while the outer compression chamber 10 b includes Do not communicate. The intermediate pressure port 125 is arranged on the inner side in the radial direction DRb of the fixed scroll 12 in the surface width Wf of the fixed base surface 121a corresponding to the mutual interval between the fixed tooth portions 122. Therefore, compared to the compressor in which the fixed side and the swivel side of the pair of scrolls 11 and 12 are reversed with respect to the present embodiment, the difference in cross-sectional area between both the tooth portions 112 and 122 shown in FIG. As can be seen, it is easy to reduce the weight of the orbiting scroll 11.

(Second Embodiment)
Next, a second embodiment will be described. In the present embodiment, differences from the first embodiment will be mainly described. Further, the same or equivalent parts as those of the above-described embodiment will be described by omitting or simplifying them. The same applies to the description of the embodiments described later.

  As shown in FIG. 13, the compressor 1 of this embodiment is a symmetric scroll compressor, but the number of turns of the swiveling tooth portion 112 and the fixed tooth portion 122, that is, the number of scroll turns, is less than two. Specifically, the scroll winding number is 1.625, that is, the winding angle is 585 deg. For example, in the present embodiment, the number of scroll turns is less than 2 due to structural limitations of the compressor 1 and characteristics of the refrigerant that is the working fluid. The fact that the number of scroll turns is less than 2 means that, as shown in FIG. It means that.

  FIG. 14 of the present embodiment is an operation diagram corresponding to FIG. 5 described above, and FIGS. 14A to 14H are cross sections of the compression mechanism unit 10 for each turning angle position in the turning movement of the turning scroll 11. Is shown.

  14 (a) to 14 (h), similarly to FIGS. 5 (a) to 5 (h), the turning angle position at which the orbiting scroll 11 completes the inflow of the refrigerant from the refrigerant suction port 36 to the compression chambers 10a and 10b. Is the 0 deg position and the revolution direction DRrt is shown as the positive direction of the turning angle position. Accordingly, FIG. 14A shows a cross section when the turning angle position of the orbiting scroll 11 is the 0 deg position, and FIG. 14B shows a cross section when the turning angle position is the 45 deg position. 14 (c) shows a cross section when the turning angle position is the 90 deg position. FIG. 14D shows a cross section when the turning angle position is a 135 deg position, FIG. 14E shows a cross section when the turning angle position is a 180 deg position, and FIG. ) Shows a cross section when the turning angle position is a 225 deg position. FIG. 14G shows a cross section when the turning angle position is 270 deg position, and FIG. 14H shows a cross section when the turning angle position is 315 deg position.

  As shown in FIG. 14A, both the outer suction completion position R1 and the inner suction completion position R2 are 0 deg positions, and this embodiment is the same as the first embodiment in this respect. However, as shown in FIG. 14 (f), the two-chamber combined position R3 in the present embodiment is a 225 deg position, which is different from the first embodiment. That is, the attitude of the orbiting scroll 11 at the suction completion positions R1 and R2 is different from the attitude of the orbiting scroll 11 at the two-chamber combined position R3.

  Since the turning angle position of the orbiting scroll 11 shown in FIG. 13 is the 0 deg position, the relative positional relationship between the orbiting tooth portion 112 and the fixed tooth portion 122 in FIG. 13 is the same as that in FIG. is there. Further, since the turning angle position of the orbiting scroll 11 shown in FIG. 15 is the 225 deg position, the relative positional relationship between the orbiting tooth portion 112 and the fixed tooth portion 122 in FIG. 15 is the same as that in FIG. is there.

  Also in the present embodiment, the intermediate pressure port 125 is a circular hole and is disposed so as to satisfy all of the first to third conditions described above. However, the port arrangement region Ap of the intermediate pressure port 125 that satisfies all the first to third conditions is different from that of the first embodiment. Specifically, the port arrangement region Ap in the present embodiment is a hatched region that intersects with each other in FIGS. 16 and 17 in the fixed base surface 121a.

  In this embodiment, the peripheral edge ALp of the port arrangement region Ap is also the same as in the first embodiment, the first curve L1, the second curve L2, the third curve L3, the fourth curve L4, the fifth curve L5, and the sixth curve. L6. However, as shown in FIGS. 13 and 15 to 17, the port arrangement region Ap of the present embodiment is composed of two closed regions which are a first region A1p and a second region A2p. The port arrangement area Ap of the first embodiment is composed of one closed area. Whether the number of closed areas constituting the port arrangement area Ap is one or two depends on each tooth portion 112, 122. It depends on the thickness and how to select the revolution radius of the orbiting scroll 11.

  The first region A1p and the second region A2p are both formed within the surface width Wf of the fixed base surface 121a corresponding to the mutual interval between the fixed tooth portions 122. The inner side port 126a can be arranged in the first area A1p, and the outer side port 126c can be arranged in the second area A2p. Of the surface width Wf of the fixed base surface 121a corresponding to the interval between the fixed tooth portions 122, the relative positional relationship between both virtual ports 126a and 126c in the radial direction DRb of the fixed scroll 12 is as shown in FIG. This is the same as the embodiment. However, in the present embodiment, the central port 126b cannot be arranged in the port arrangement area Ap.

  Further, the peripheral edge ALp of the port arrangement area Ap is composed of the peripheral edge of the first area A1p and the peripheral edge of the second area A2p, and the peripheral edge of the first area A1p is the second curve L2 and the fourth curve as shown in FIG. It consists of a curve L4 and a sixth curve L6. And as shown in FIG. 17, the periphery of 2nd area | region A2p is comprised from the 1st curve L1, the 3rd curve L3, and the 5th curve L5.

  FIG. 18 shows the change in the volume Vi of the inner compression chamber 10a, the change in the volume Vo of the outer compression chamber 10b, and the total of both the compression chambers 10a and 10b in the compressor 1 of the present embodiment. The change of the volume Vio is shown. FIG. 19 shows the change in the pressure Pi of the inner compression chamber 10a, the change in the pressure Po of the outer compression chamber 10b, and the compression chambers 10a and 10b in the compressor 1 of the present embodiment. The change of the pressure Pio after the two-chamber combination is shown. The vertical axis and horizontal axis in FIG. 18 are the same as those in FIG. 7, and the vertical axis and horizontal axis in FIG. 19 are the same as those in FIG.

  In the present embodiment, as described above, the scroll winding number is smaller than that in the first embodiment. Therefore, as shown in FIG. 18, in this embodiment, the timing at which the change in the volume of the inner compression chamber 10a and the change in the volume of the outer compression chamber 10b begin to differ is early. As a result, as shown in FIG. 19, the mutual pressure difference between the compression chambers 10 a and 10 b also starts at an earlier timing than in the first embodiment. The amount of gas injection from the intermediate pressure port 125 is determined by the opening area of the intermediate pressure port 125 and the pressure difference between the compression chambers 10a and 10b with respect to the intermediate pressure Pm. Therefore, it can be seen from FIGS. 18 and 19 that the gas injection amount can be increased by opening the intermediate pressure port 125 in preference to the inner compression chamber 10a rather than the outer compression chamber 10b.

  A solid line Lim in FIG. 20A represents a change in the opening area of the inner-side port 126a with respect to the inner compression chamber 10a. As shown in FIG. 20A, the inner side port 126a opens to the inner compression chamber 10a, but does not open to the outer compression chamber 10b. 20A is the same as FIG. 11A, and the vertical and horizontal axes in FIG. 20B are the same as those in FIG. 11C.

  A broken line Lom in FIG. 20B represents a change in the opening area of the outer side port 126c with respect to the outer compression chamber 10b. As shown in FIG. 20B, the outer side port 126c opens to the outer compression chamber 10b, but does not open to the inner compression chamber 10a.

  As shown in FIG. 20A and FIG. 20B, both the inner side port 126a and the outer side port 126c are determined from the timing of completion of suction from the supply unit 14 to both the compression chambers 10a and 10b, as in the first embodiment. The compression chambers 10a and 10b begin to open. Then, both the inner side port 126a and the outer side port 126c are closed immediately before the two-chamber combination where the compression chambers 10a and 10b communicate with each other, and the opening to the compression chambers 10a and 10b is completed.

  FIG. 21 shows the amount of gas injection from each of the two virtual ports 126a and 126c into the compression chambers 10a and 10b, and the amount of gas injection from the inner port 126a as 1. In FIG. 21, (i) the refrigerant supply amount from the inner side port 126a and (ii) the refrigerant supply amount from the outer side port 126c are displayed in order from the left side. As can be seen from FIG. 21, the gas injection amount from the inner port 126a is larger than the gas injection amount from the outer port 126c. This is the same as in the first embodiment.

  However, the difference between the gas injection amount from the outer port 126c and the gas injection amount from the inner port 126a is larger than that in the first embodiment. Thus, in order to increase the amount of gas injection from the intermediate pressure port 125, it is effective to dispose the intermediate pressure port 125 closer to the position of the inner side port 126a as the number of scroll turns decreases.

  In consideration of the above, in the compressor 1 of the present embodiment, the intermediate pressure port 125 is disposed at the position of the inner side port 126a.

  In the present embodiment, as in the first embodiment, all of the first to third conditions described above are satisfied, so that both the compression chambers 10a and 10b communicate with each other as the orbiting scroll 11 turns. Prior to merging, the intermediate pressure port 125 is closed by the orbiting scroll 11. Therefore, re-expansion corresponding to the dead volume of the intermediate pressure port 125 is suppressed, which is effective in improving the efficiency of the compressor 1. This is an effect obtained in the first embodiment, but can be obtained more prominently in the present embodiment. The dead volume is the volume of the refrigerant passage between the open end 125a of the intermediate pressure port 125 and the check valve 50 in FIG.

  Except as described above, the present embodiment is the same as the first embodiment. And in this embodiment, the effect show | played from the structure common to the above-mentioned 1st Embodiment can be acquired similarly to 1st Embodiment.

(Third embodiment)
Next, a third embodiment will be described. In the present embodiment, differences from the second embodiment will be mainly described.

  As described in the first and second embodiments, since the intermediate pressure port 125 needs to be closed by the tip surface 112c of the swivel tooth portion 112, the opening end 125a of the intermediate pressure port 125 is connected to the swivel tooth portion 112. It cannot be increased beyond the thickness TKr. Therefore, this limits the opening area of the intermediate pressure port 125 with respect to the inner compression chamber 10a or the outer compression chamber 10b, and may cause a contradiction that the opening area is insufficient at the timing when the intermediate pressure port 125 is opened.

  In other words, the port arrangement area Ap indicating the range in which the intermediate pressure port 125 can be arranged varies depending on the specifications of the scrolls 11 and 12, but as a tendency, the port arrangement area Ap becomes narrower as the scroll winding number is smaller. When the intermediate pressure port 125 is to be arranged in the narrow port arrangement region Ap, if the intermediate pressure port 125 is, for example, a simple circular hole, the opening of the intermediate pressure port 125 to the inner compression chamber 10a or the outer compression chamber 10b. The area may be insufficient.

  Further, if the open end 125a of the intermediate pressure port 125 is assumed to be a simple circular shape, from the start of communication of the intermediate pressure port 125 to any one of the compression chambers 10a, 10b until the fully open state for that compression chamber 10a, 10b. During this period, the refrigerant flow from the intermediate pressure port 125 is likely to be throttled. This is because when the intermediate pressure port 125 is fully opened, the entire circular shape of the opening end 125a is exposed to the compression chambers 10a and 10b, but in the middle of the period until the fully open state, an arc that is a part of the circular shape is formed. This is because it is only exposed to the compression chambers 10a and 10b.

  Based on this, as shown in FIGS. 22 and 23, the intermediate pressure port 125 of the present embodiment is not a circular hole but a flat shape. That is, the open end 125 a of the intermediate pressure port 125 is formed to extend in the spiral direction DRg of the fixed tooth portion 122. The open end 125a of the intermediate pressure port 125 does not protrude from the first region A1p, which is a part of the port arrangement region Ap, and is accommodated in the first region A1p. It is the same as that of 2nd Embodiment to be arrange | positioned in this position.

  In addition, the intermediate pressure port 125 of the present embodiment is one long hole as shown in FIG. 23. For example, the intermediate pressure port 125 has the characteristics shown in FIGS. It does not matter if it is a hole with a shape. Further, the intermediate pressure port 125 does not have to be a single hole, and may be provided as a set of a plurality of holes, for example. Each of the plurality of holes may be a circular hole, a long hole, or an elliptical hole, and the size of each of the plurality of holes may be different.

  Specifically, in the present embodiment, as shown in FIGS. 23 and 24, the fixed base surface 121 a has a port edge 125 b that forms the opening end 125 a of the intermediate pressure port 125. And the port edge 125b has the inner edge part 125c arrange | positioned inside the radial direction DRb of the fixed scroll 12, and the outer edge part 125d arrange | positioned on the outer side of the radial direction DRb. The inner edge portion 125c and the outer edge portion 125d are formed so as to extend in the spiral direction DRg of the fixed tooth portion 122, as shown in FIGS.

  In the present embodiment, the intermediate pressure port 125 communicates with the inner compression chamber 10 a as the turning scroll 11 turns. The inner edge 125c of the port end edge 125b of the intermediate pressure port 125 is the tip surface of the swivel tooth portion 112 of the port end edge 125b at the start of communication when the intermediate pressure port 125 starts to communicate with the inner compression chamber 10a. This is the portion closest to the inner side edge 112d. Further, the inner edge portion 125c forms a shape along the front end surface inner side edge 112d at the start of communication where the intermediate pressure port 125 starts to communicate with the inner compression chamber 10a.

  In the present embodiment, a solid line L1im in FIG. 25 represents a change in the opening area of the intermediate pressure port 125 with respect to the inner compression chamber 10a. For comparison, a broken line Lim is also shown in FIG. 25, and the broken line Lim in FIG. 25 is the same as the solid line Lim in FIG. 20A. That is, a broken line Lim in FIG. 25 indicates an opening area when the intermediate pressure port 125 is a circular hole instead of the hole shape of FIG. Note that the width in the radial direction DRb of the fixed scroll 12 is the same regardless of the hole shape of FIG. 22 or the circular hole. Also, the vertical and horizontal axes in FIG. 25 are the same as those in FIG. 20A.

  Except as described above, the present embodiment is the same as the second embodiment. And in this embodiment, the effect show | played from the structure common to the above-mentioned 2nd Embodiment can be acquired similarly to 2nd Embodiment.

  Further, according to the present embodiment, as shown in FIGS. 22 and 23, the inner edge 125c of the port edge 125b is connected to the port edge 125b when the intermediate pressure port 125 starts to communicate with the inner compression chamber 10a. Of these, the portion closest to the inner edge 112d of the distal end surface of the swivel tooth portion 112 is provided. The inner edge portion 125c forms a shape along the front end surface inner side edge 112d at the start of communication when the intermediate pressure port 125 starts to communicate with the inner compression chamber 10a. Therefore, compared with the case where the opening end 125a of the intermediate pressure port 125 has a simple circular shape, for example, the rising of the gas injection amount can be accelerated at the initial opening of the intermediate pressure port 125 with respect to the inner compression chamber 10a. This can also be seen from comparing the solid line L1im and the broken line Lim with the change in the opening area of FIG.

  Further, according to the present embodiment, as shown in FIGS. 22 and 23, the opening end 125a of the intermediate pressure port 125 is formed to extend in the spiral direction DRg of the fixed tooth portion 122 in the first region A1p. Yes. Therefore, when the intermediate pressure port 125 is fully opened, the opening area of the intermediate pressure port 125 is increased with respect to the communication compression chamber that communicates with the gas injection port in accordance with the orbital movement of the orbiting scroll 11 among the compression chambers 10a and 10b. Is possible.

  In addition, although this embodiment is a modification based on 2nd Embodiment, it is also possible to combine this embodiment with the above-mentioned 1st Embodiment.

(Other embodiments)
(1) In each of the embodiments described above, for example, as shown in FIG. 3, the compressor 1 is a symmetric scroll compressor, but this is an example. For example, the compressor 1 may be an asymmetric scroll compressor such as the compressor of Patent Document 1 in which the winding end angle of the swivel tooth portion 112 and the winding end angle of the fixed tooth portion 122 are different from each other. I can think.

  As such, if the compressor 1 is an asymmetric scroll compressor, unlike the above-described embodiments, the outer suction completion position R1 is the same as the inner suction completion position R2 in the orbiting movement of the orbiting scroll 11. Don't be. However, even in the asymmetric scroll compressor, the first curve L1 in FIG. 9 is still a curve that constitutes a part of the front end surface outer side edge 112e of the orbiting scroll 11 at the outer suction completion position R1. The sixth curve L6 is still a curve constituting a part of the front end surface inner side edge 112d of the orbiting scroll 11 at the inner suction completion position R2.

  (2) In each of the embodiments described above, the fluid sucked by the compressor 1 is, for example, carbon dioxide as a refrigerant, but may be a fluid other than carbon dioxide as long as it is a compressible fluid. Further, the compressor 1 may not be used for the refrigeration cycle 100.

  (3) In each of the above-described embodiments, for example, the intermediate pressure port 125 shown in FIG. 3 communicates with the inner compression chamber 10a every rotation of the orbiting scroll 11 and does not communicate with the outer compression chamber 10b. Not limited to. For example, the intermediate pressure port 125 may communicate with the outer compression chamber 10b as long as it does not communicate with the inner compression chamber 10a. In short, the intermediate pressure port 125 communicates with at least one of the compression chambers 10a and 10b for each rotation of the orbiting scroll 11, and the refrigerant that is in the middle of compression in the communication compression chamber communicates with the refrigerant from the outside. May be a port that joins.

  (4) In the first embodiment described above, as shown in FIG. 3, one scroll 11 of the pair of scrolls 11, 12 is a turning scroll that turns and the other scroll 12 does not turn. However, this relationship may be reversed. That is, one scroll 11 shown in FIG. 3 may be a fixed scroll and the other scroll 12 may be a turning scroll. If it did so, one compression chamber 10a of a pair of compression chambers 10a and 10b shown in FIG. 3 will become an outer compression chamber located in the radial direction outer side of the turning tooth part which the other scroll 12 has. . The other compression chamber 10b is an inner compression chamber located on the radially inner side of the swivel tooth portion. The same applies to the second and third embodiments.

  (5) In each of the embodiments described above, for example, as shown in FIG. 3, the intermediate pressure port 125 is a single hole, but it may be composed of a plurality of holes provided densely in one place.

  (6) In the third embodiment described above, as shown in FIG. 22 and FIG. 23, the intermediate pressure port 125 communicates with the inner compression chamber 10a as the orbiting scroll 11 turns, whereas the intermediate pressure port 125 communicates with the outer compression chamber 10b. Does not communicate. However, this is an example.

  For example, when the scroll winding number is large, for example, when there are two or more windings, depending on the configuration of the compressor 1, the intermediate pressure port 125 is alternately switched between the inner compression chamber 10 a and the outer compression chamber 10 b as the orbiting scroll 11 turns. Some communicate with. That is, there is a case where the intermediate pressure port 125 communicates with the outer compression chamber 10b when the orbiting scroll 11 does not communicate with the inner compression chamber 10a. In such a compressor 1, the outer edge portion 125d of the port end edge 125b of the intermediate pressure port 125 has the swivel tooth of the port end edge 125b at the start of communication when the intermediate pressure port 125 starts to communicate with the outer compression chamber 10b. The portion 112 is closest to the outer edge 112e on the front end surface. Therefore, in the compressor 1 in which the intermediate pressure port 125 communicates with the outer compression chamber 10b, the outer edge portion 125d of the intermediate pressure port 125 is connected to the outer edge 112e of the front end surface at the start of communication when the intermediate pressure port 125 starts communicating with the outer compression chamber 10b. It is good to form along.

  (7) In each of the embodiments described above, the refrigeration cycle 100 in FIG. 1 constitutes a part of the hot water supply system, but is not limited thereto. For example, a part of a heat pump system for a vehicle air conditioner or a heat pump system for other industrial or household air conditioners may be configured.

  (8) In each of the embodiments described above, as shown in FIG. 2, the compressor 1 is a vertical type, but may be a horizontal type.

  (9) It should be noted that the present invention is not limited to the above-described embodiment, and can be implemented with various modifications. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible.

  In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case.

  In each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified, or in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship, etc. are not limited.

(Summary)
According to the first aspect shown in part or all of each of the above embodiments, in the scroll compressor, one of the inner compression chamber and the outer compression chamber is accompanied by the orbiting movement of the orbiting scroll. The volume changes more slowly than the other compression chamber. And it arrange | positions in the site | part which communicates for a long time to said one compression chamber rather than said other compression chamber among fixed base surfaces of a fixed scroll.

  Moreover, according to the 2nd viewpoint, the gas injection port is provided in one place of the fixed base | substrate surfaces. Therefore, the mechanical structure related to the gas injection port can be simplified as compared with the case where the gas injection port is provided at a plurality of locations.

  According to the third aspect, the gas injection port starts to communicate with the communication compression chamber after the completion of suction during the compression period of the communication compression chamber communicating with the gas injection port. During the compression period, the communication between the gas injection port and the communication compression chamber is blocked until the inner compression chamber and the outer compression chamber begin to communicate with each other. Accordingly, it is possible to reduce waste in the fluid supply from the gas injection port. The waste is, for example, that the fluid from the gas injection port flows to the supply unit, or that the gas injection port prevents the pressure increase in one of the inner compression chamber and the outer compression chamber.

  Moreover, according to the 4th viewpoint, the gas injection port is opened so that it may be settled in the port arrangement | positioning area | region comprised from the 1 or 2 closed area | region among fixed base | substrate surfaces. The peripheral edge of the port arrangement region has a first curve, a second curve, a third curve, a fourth curve, a fifth curve, and a sixth curve. The first curve is a curve constituting a part of the outer edge on the front end surface of the orbiting scroll at the outer suction completion position. Moreover, a 2nd curve is a 2nd curve which comprises a part of front end surface inner side edge of the turning scroll in a two-chamber united position. Further, the third curve is a curve constituting a part of a curve that is spaced by the thickness of the swivel tooth portion while maintaining an equal interval from the inner edge of the base end to the radially inner side of the fixed scroll. Further, the fourth curve is a curve constituting a part of the curve that is spaced apart by the thickness of the swivel tooth portion while maintaining an equal interval from the base side outer side edge to the radially outer side of the fixed scroll. Further, the fifth curve is a curve constituting a part of the outer edge on the front end surface of the orbiting scroll at the two-chamber combined position. Further, the sixth curve is a curve constituting a part of the inner edge on the front end surface of the orbiting scroll at the inner suction completion position. Therefore, by opening the gas injection port so as to be within the port arrangement region, it is possible to reduce waste in the fluid supply from the gas injection port described above.

  Further, according to the fifth aspect, the orbiting scroll orbits so as to reach the inner suction completion position at the same timing as it reaches the outer suction completion position.

  Moreover, according to the 6th viewpoint, a port arrangement | positioning area | region is one closed area | region extended in the spiral direction along the spiral shape of a fixed tooth part. And the gas injection port is arrange | positioned in the position close | similar to one side of the spiral direction among port arrangement | positioning area | regions. Therefore, it is possible to increase the fluid supply amount from the gas injection port, that is, the gas injection amount, as compared with the case where the gas injection port is arranged in the center of the spiral direction in the port arrangement region.

  According to the seventh aspect, the fixed base surface of the fixed scroll has a port end edge that forms an open end of the gas injection port. When the gas injection port starts to communicate with the inner compression chamber, a portion of the port edge closest to the inner edge of the distal end surface forms a shape along the inner edge of the distal end surface. Therefore, compared with the case where the opening end of the gas injection port has a simple circular shape, for example, the rising of the gas injection amount can be accelerated at the initial opening of the gas injection port with respect to the inner compression chamber.

  Further, according to the eighth aspect and the ninth aspect, when the gas injection port starts to communicate with the outer compression chamber, a portion of the port edge closest to the outer edge on the distal end surface is the tip of the port edge. Forms a shape along the outer side edge. Therefore, compared with the case where the opening end of the gas injection port has a simple circular shape, for example, the rising of the gas injection amount can be accelerated at the initial opening of the gas injection port with respect to the outer compression chamber.

  According to the tenth aspect, the open end of the gas injection port is formed to extend in a spiral direction along the spiral shape of the fixed tooth portion. Accordingly, when the gas injection port is fully opened, the opening area of the gas injection port can be increased with respect to the communication compression chamber that communicates with the gas injection port in accordance with the orbiting scroll of the inner compression chamber and the outer compression chamber. Is possible.

  According to the eleventh aspect, the gas injection port communicates with the inner compression chamber as the orbiting scroll moves, but does not communicate with the outer compression chamber. The gas injection port is arranged on the inner side in the radial direction of the fixed scroll in the surface width of the fixed base surface corresponding to the interval between the fixed tooth portions.

DESCRIPTION OF SYMBOLS 10a Inner compression chamber 10b Outer compression chamber 11 Orbiting scroll 12 Fixed scroll 111 Orbit base part 112 Orbiting tooth part 121 Fixed base part 121a Fixed base surface 122 Fixed tooth part 125 Intermediate pressure port

Claims (11)

A scroll compressor that discharges after compressing the fluid,
A fixed scroll (12) having a fixed base part (121) and a fixed tooth part (122) protruding from the fixed base part and having a spiral shape;
An orbiting scroll (11) having an orbiting base portion (111) and an orbiting tooth portion (112) projecting from the orbiting base portion and having a spiral shape, and orbiting about a single axis (C1) with respect to the fixed scroll. )
The fixed tooth part and the swivel tooth part engage with each other, and are located on the radially inner side of the swivel tooth part and compressed on the fluid, and located on the radially outer side of the swivel tooth part. And an outer compression chamber (10b) for compressing the fluid is formed between the fixed tooth part and the swivel tooth part, respectively.
The orbiting scroll moves the inner compression chamber and the outer compression chamber inward in the radial direction along with the orbiting movement of the orbiting scroll, and reduces the volume of the inner compression chamber and the volume of the outer compression chamber. ,
One compression chamber of the inner compression chamber and the outer compression chamber changes in volume more slowly than the other compression chamber as the orbiting scroll revolves.
The fixed base portion has a fixed base surface (121a) formed between the fixed tooth portions and opposed to a distal end surface (112c) of the swivel tooth portion. A gas injection port (125) that is blocked by being covered with the tip surface is formed,
The gas injection port is
Do not communicate with the inner compression chamber and the outer compression chamber at the same time,
At least one of the inner compression chamber and the outer compression chamber communicates with each rotation of the orbiting scroll, and the fluid from outside joins the fluid that is being compressed in the communication compression chamber. Let
The scroll compressor arrange | positioned among the said fixed base | substrate surfaces at the site | part connected to said one compression chamber for a long time rather than said other compression chamber.   The scroll compressor according to claim 1, wherein the gas injection port is provided at one of the fixed base surfaces. A supply section (14) for supplying the fluid to the inner compression chamber and the outer compression chamber;
During the compression period in which the fluid is compressed in the communication compression chamber that communicates with the gas injection port in accordance with the orbiting movement of the orbiting scroll among the inner compression chamber and the outer compression chamber, the communication compression chamber and the supply are supplied. Starting from the point of completion of suction when the flow of the fluid from the supply unit to the communication compression chamber is completed by blocking communication with the unit,
During the compression period, the inner compression chamber and the outer compression chamber begin to communicate with each other,
The gas injection port starts to communicate with the communication compression chamber after the completion of the suction during the compression period, and communication between the gas injection port and the communication compression chamber is established between the inner compression chamber and the outer compression chamber. The scroll compressor according to claim 1 or 2, wherein the scroll compressor is shut off before the chamber starts to communicate with each other. A supply section (14) for supplying the fluid to the inner compression chamber and the outer compression chamber;
The orbiting scroll shuts off the communication between the outer compression chamber and the supply unit when the orbiting angular position in the orbiting movement of the orbiting scroll reaches a predetermined outer suction completion position (R1). Communication between the inner compression chamber and the supply unit when the inflow of the fluid from the supply unit to the outer compression chamber is completed and the turning angle position reaches a predetermined inner suction completion position (R2). And when the fluid flow from the supply section to the inner compression chamber is completed and the swivel angle position reaches a predetermined two-chamber combined position (R3), the inner compression chamber and Begin to communicate with the outer compression chamber,
The tip surface of the swivel tooth portion has a tip surface inner side edge (112d) on the radially inner side of the tip surface and a tip surface outer side edge (112e) on the radially outer side of the tip surface,
The base end (122c) of the fixed tooth portion has a base end inner side edge (122d) on the radially inner side of the base end and a base end outer side edge (122e) on the radially outer side of the base end. And
The gas injection port is opened so as to be within a port arrangement region (Ap) constituted by one or two closed regions of the fixed base surface,
A peripheral edge (ALp) of the port arrangement region is located at the first curve (L1) constituting a part of the outer edge of the orbiting scroll at the outer suction completion position and the two-chamber combined position. A second curve (L2) that constitutes a part of the inner edge of the distal end surface of the orbiting scroll and the inner diameter of the fixed scroll radially inward with respect to the inner edge of the proximal end while maintaining an equal interval A third curve (L3) constituting a part of a curve separated by a thickness (TKr) and the radially outer side of the fixed scroll are maintained at equal intervals with respect to the base side outer side edge, and the swivel tooth portion A fourth curve (L4) that constitutes a part of a curve separated by the thickness, and a fifth curve (L5) that constitutes a part of the outer edge on the front end surface of the orbiting scroll at the two-chamber combined position; The orbiting scroll at the inner suction completion position Sixth curve (L6) and a scroll compressor according to claim 1 or 2 having a forming part of serial distal end surface inner edge.   The scroll compressor according to claim 4, wherein the orbiting scroll revolves so as to reach the inner suction completion position at the same timing as the outer suction completion position. The port arrangement region is one closed region extending in a spiral direction (DRg) along the spiral shape of the fixed tooth portion,
The scroll compressor according to claim 4 or 5, wherein the gas injection port is disposed at a position close to one side in the spiral direction in the port arrangement region. The tip surface of the swivel tooth has a tip surface inner side edge (112d) on the radially inner side of the tip surface,
The gas injection port communicates with the inner compression chamber along with the orbiting movement of the orbiting scroll,
The fixed base surface has a port end edge (125b) that forms an open end (125a) of the gas injection port;
At the start of communication when the gas injection port starts to communicate with the inner compression chamber, a portion (125c) of the port edge closest to the inner edge of the tip surface has a shape along the inner edge of the tip surface. The scroll compressor according to any one of claims 1 to 3. The tip surface of the swivel tooth has a tip surface outer side edge (112e) on the radially outer side of the tip surface,
The gas injection port communicates with the outer compression chamber when it does not communicate with the inner compression chamber as the orbiting scroll is revolving.
When the gas injection port starts to communicate with the outer compression chamber, a portion (125d) of the port end edge that is closest to the outer edge of the distal end surface is shaped along the outer edge of the distal end surface. The scroll compressor of Claim 7 which comprises these. The tip surface of the swivel tooth has a tip surface outer side edge (112e) on the radially outer side of the tip surface,
The gas injection port communicates with the outer compression chamber along with the orbiting movement of the orbiting scroll,
The fixed base surface has a port end edge (125b) that forms an open end (125a) of the gas injection port;
At the start of communication when the gas injection port starts to communicate with the outer compression chamber, a portion (125d) of the port edge closest to the outer edge of the distal end surface has a shape along the outer edge of the distal end surface. The scroll compressor according to any one of claims 1 to 3.   The scroll compressor according to any one of claims 7 to 9, wherein an opening end of the gas injection port is formed so as to extend in a spiral direction (DRg) along the spiral shape of the fixed tooth portion. The gas injection port communicates with the inner compression chamber along with the orbiting movement of the orbiting scroll, but does not communicate with the outer compression chamber,
The said gas injection port is arrange | positioned inside radial direction (DRb) of the said fixed scroll among surface width (Wf) of the said fixed base | substrate surface corresponding to the mutual space | interval of the said fixed tooth part. The scroll compressor according to any one of 7.

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