JP6186973B2 - Refrigerant compressor - Google Patents

Description

  The present invention relates to a refrigerant compressor provided in an air conditioner.

  Conventionally, air conditioners that employ an injection cycle are known. The injection cycle is a refrigeration cycle in which a gas refrigerant having an intermediate pressure between the heat exchanger of the outdoor unit and the heat exchanger of the indoor unit is returned to the compression chamber of the scroll compressor, and the efficiency of the refrigeration cycle It is intended to improve. The scroll compressor includes a swivel-type movable scroll having a spiral wall body and a fixed scroll having a spiral wall body, and has a variable volume having a spiral shape formed between the movable scroll and the fixed scroll. It has a compression chamber. The compression chamber compresses the gas refrigerant by reducing the volume while moving from the outer peripheral portion to the central portion by turning the movable scroll, and finally communicates with the discharge port drilled in the central portion of the fixed scroll. High-pressure refrigerant is discharged from the discharge port. In the scroll compressor compatible with the injection cycle, an injection port is formed at a radial intermediate position of the fixed scroll in order to inject a gas refrigerant having an intermediate pressure into the compression chamber. The compression chamber communicates with the injection port at a position on the way from the outer peripheral portion to the central portion, and a gas refrigerant having an intermediate pressure is injected from the injection port.

  A reed valve is provided at the refrigerant inflow portion to the injection port. The reed valve is a check valve composed of a plate-like valve body, and allows the flow of gas refrigerant supplied from the injection pipe in the direction toward the compression chamber and prevents the flow of gas refrigerant in the opposite direction. Therefore, when the compression chamber communicates with the injection port, if the pressure in the compression chamber is lower than the intermediate pressure supplied from the injection pipe, the reed valve is opened and the gas refrigerant is injected into the compression chamber.

  The reed valve is provided in the valve chamber 501 as shown in FIG. The valve chamber 501 includes a retainer 502 that receives the back surface of the reed valve 500 and holds the reed valve 500 when the reed valve 500 is opened, and a seating surface 503 on which the reed valve 500 is seated. The seating surface 503 is formed with an inlet opening 504 for introducing a gas refrigerant (referred to as injection refrigerant) supplied from the injection pipe into the valve chamber 501. The inlet opening 504 communicates with the injection pipe via the injection refrigerant introduction passage 505. Further, an outlet opening 506 for supplying the injection refrigerant introduced into the valve chamber 501 to the injection port 511 formed in the fixed scroll 510 is formed on the surface of the valve chamber 501 facing the seating surface 503. . The outlet opening 506 communicates with the injection port 511 through the injection refrigerant supply passage 507.

  The injection refrigerant introduction passage 505 is provided in a direction parallel to the compressor shaft. Further, the reed valve 500 is provided so that its plate surface is in a direction perpendicular to the compressor shaft. When the reed valve 500 is opened, the injection refrigerant flows into the valve chamber 501 from the inlet opening 504. The injection refrigerant that has flowed into the valve chamber 501 is guided to the front (the free end side of the reed valve 500) by the reed valve 500 as shown by an arrow, and then flows into the space formed on the back surface of the retainer 502 to the outlet. It passes through the opening 506 and is sent to the compression chamber 512.

  Patent Document 1 proposes another check valve structure provided in the injection refrigerant passage. In this Patent Document 1, a valve unit is proposed in which a reed valve is disposed in a through hole that passes through a fixed scroll that is an injection refrigerant passage in parallel to the axial direction, and the reed valve is opened and closed in a direction orthogonal to the axial direction. ing. In this valve unit, one end of the reed valve is sandwiched and fixed between the unit main body and the valve pressing member, and the other end of the reed valve is provided as a free end so as to be openable and closable with respect to the seating surface. The fixed end of the reed valve is provided on the downstream side of the through hole, and the free end is provided on the upstream side of the through hole. Accordingly, in order to open the free end of the reed valve and allow the injection refrigerant flowing into the valve unit to flow downstream, the inner circumferential surface of the through hole is formed on both sides of the valve pressing member along the longitudinal direction of the reed valve. A space is formed between and the injection refrigerant is supplied to the compression chamber through this space.

JP 2009-287512 A

(Problems to be solved by the invention)

  However, in the reed valve structure shown in FIG. 9, the volume of the valve chamber 501 is increased. The volume of the valve chamber 501 causes a reduction in the compression efficiency of the compressor, and is generally called a recompression volume. Therefore, in the reed valve structure, the recompression volume cannot be reduced, and the compression efficiency of the compressor is reduced. Further, since the valve chamber area in the direction orthogonal to the compressor shaft is increased, the layout becomes difficult when a plurality of reed valves are arranged.

  Further, in the valve unit proposed in Patent Document 1, it is necessary to form a space extending along the longitudinal direction of the reed valve on both sides of the valve pressing member, and to flow the injection refrigerant into this space, and the flow resistance is It gets bigger. Moreover, the volume of the space formed on both sides of the valve pressing member becomes the recompression volume, and the recompression volume is increased accordingly. Therefore, the compression efficiency is reduced. In addition, since the shape of the flow path through which the injection refrigerant flows is complicated, the pressure loss is also increased in this respect, which causes a reduction in compression efficiency.

  An object of the present invention is to solve the above problems and improve the compression efficiency of a refrigerant compressor.

(Means for solving the problem)
The feature of the present invention that solves the above problems is as follows.
A housing (10), a fixed scroll (20) fixed in the housing and formed with a spiral wall, and a movable scroll (form) having a spiral wall formed in the housing and orbiting relative to the fixed scroll ( 30) and a compression chamber (80) for compressing and discharging the low-pressure refrigerant sucked by the orbiting motion of the movable scroll, which is formed between the spiral wall of the fixed scroll and the spiral wall of the movable scroll. And an injection port (71) for introducing an intermediate-pressure refrigerant in the refrigerant circuit through which the refrigerant discharged from the compression chamber flows, and an introduction path for introducing the refrigerant into the injection port, functioning as a check valve In the refrigerant compressor provided with the reed valve portion (90)
The reed valve portion includes a plate-shaped reed valve body (93) having one end as a fixed end and the other end as a free end, and a retainer ( 92), a refrigerant inlet (95) is formed, the reed valve body is seated when the valve is closed, and a seating surface (94) that covers the inlet, and the reed valve is formed between the seating surface and the retainer. A valve chamber (97) that becomes a movable space of the main body,
The reed valve body is arranged such that the free end is closer to the compression chamber than the fixed end, and the direction connecting the fixed end and the free end is parallel to the compressor shaft ,
An introduction path communicating with the inlet is formed in parallel with a plane orthogonal to the compressor shaft;
The valve chamber is formed with an outlet (98) for sending the refrigerant to the injection port in a direction from the fixed end to the free end of the reed valve body.

  The refrigerant compressor of the present invention is a scroll type compressor, and includes an injection port for introducing an intermediate-pressure refrigerant in the refrigerant circuit into the compression chamber. The intermediate pressure is lower than the discharge pressure of the compressor and higher than the suction pressure. A reed valve portion is provided in the introduction path for introducing the refrigerant into the injection port. The reed valve portion functions as a check valve that allows the refrigerant to flow from the outside (refrigerant circuit) to the injection port and prevents the refrigerant from flowing out from the injection port. In the reed valve portion, a refrigerant inlet is formed on the seating surface, the free end side of the reed valve main body is disposed at the inlet, and the valve is closed by closing the inlet with the plate surface of the reed valve main body. When the reed valve body is bent and opened due to the pressure difference, the back surface of the reed valve body is held by the retainer. A space formed between the seating surface and the retainer, that is, a movable space of the reed valve body serves as a valve chamber.

  The reed valve main body is arranged in a direction in which the free end is closer to the compression chamber than the fixed end. Further, the valve chamber is formed with an outlet for sending the refrigerant to the injection port in a direction from the fixed end of the reed valve main body toward the free end. For this reason, the refrigerant flowing from the inlet is guided to the reed valve main body and smoothly flows to the outlet. And the refrigerant | coolant sent out from the exit goes to the compression chamber side. For this reason, the channel | path which flows a refrigerant | coolant to the side surface and back surface of a retainer (a side surface and back surface when the holding surface holding a reed valve main body is made into the front) is not required. Therefore, the volume of the passage through which the refrigerant flows in the reed valve portion can be made substantially the same as the movable space of the reed valve body, for example. Thereby, the recompression volume can be reduced. Further, the passage through which the refrigerant flows in the reed valve portion becomes simple, and the pressure loss can be reduced. As a result, according to the present invention, the compression efficiency of the refrigerant compressor can be improved.

  In the present invention, the reed valve body is arranged so that the direction connecting the fixed end and the free end of the reed valve body is parallel to the compressor shaft. Further, the introduction path communicating with the inlet is formed in parallel with the plane orthogonal to the compressor shaft. Here, the direction connecting the fixed end and the free end of the reed valve body is the direction formed by the line connecting the width direction center of the fixed end and the width direction center of the free end when the reed valve body is closed. It corresponds to. The compressor shaft corresponds to the turning center axis of the movable scroll. According to this configuration, since the plate surface of the reed valve main body is disposed so as to be parallel to the compressor shaft, the area occupied by the reed valve main body in the direction orthogonal to the compressor shaft can be minimized. Therefore, when providing a plurality of other reed valve portions, their layout becomes easy. In particular, in addition to the reed valve portion of the present invention, when another reed valve portion is provided so that the plate surface of the reed valve main body is orthogonal to the compressor shaft, the layout is excellent.

It is a schematic structure figure showing notionally the section of the scroll type compressor concerning this embodiment. It is a figure showing the back surface of a fixed scroll. It is the schematic of the cross section orthogonal to the compressor axis | shaft in the position (AA cutting | disconnection line position of FIG. 1) in which the reed valve unit for injection is provided. It is a side view of the reed valve unit for injection. It is a see-through | perspective perspective view showing the valve chamber of the reed valve unit for injection. It is the schematic of the cross section orthogonal to the compressor axis | shaft in the position (BB cutting line position of FIG. 1) in which the valve part for discharge is provided. It is the arrangement figure which expressed arrangement of each part of a valve mechanism seeing from the direction of an axis. It is a schematic block diagram of the air conditioner to which the refrigerant compressor of this embodiment is applied. It is sectional drawing showing the conventional reed valve part for injection.

  Hereinafter, embodiments of the refrigerant compressor of the present invention will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram conceptually showing a cross section of the scroll compressor according to the present embodiment. A scroll compressor (hereinafter simply referred to as a compressor) 1 includes a housing 10, a fixed scroll 20 fixed in the housing 10, a movable scroll 30 engaged with the fixed scroll 20, and a swivel of the movable scroll 30. A shaft 40 to be moved and a clutch pulley 50 that transmits a rotational force to the shaft 40 are provided.

  The fixed scroll 20 has a disk-shaped main body 21 and a spiral wall body 22 standing from one side of the main body 21 and is fixed to the housing 10 by screws (not shown). The main body 21 has one discharge port 61 and two relief ports 62a and 62b (first relief port 62a and second relief port 62b), which are through holes bored in the axial direction at the position shown in FIG. ) Two reduce ports 63a, 63b (first reduce port 63a, second reduce port 63b), two heating injection ports 71a, 71b (first heating injection port 71a, second heating injection port 71b), Two cooling injection ports 72a and 72b (a first cooling injection port 72a and a second cooling injection port 72b) are formed. In this specification, “axial direction” means the axial direction of the compressor 1 (the axial direction of the shaft 40) unless otherwise specified.

  In FIG. 1, the discharge port 61, the 2nd reduction port 63b, and the 1st heating injection port 71a are shown as an example. The position of each port viewed from the axial direction is as shown in FIG. Hereinafter, when the two relief ports 62a and 62b are not distinguished from each other, they are simply referred to as a relief port 62. When the two reduce ports 63a and 63b are not distinguished from each other, they are simply referred to as a reduce port 63. When the two heating injection ports 71a and 71b are not distinguished from each other, they are simply referred to as a heating injection port 71. When the two cooling injection ports 72a and 72b are not distinguished from each other, they are simply used for cooling. This is called an injection port 72. In addition, when the heating injection port 71 and the cooling injection port 72 are not distinguished, they are simply referred to as an injection port 70.

  The movable scroll 30 includes a disk-shaped main body portion 31, a spiral wall body 32 erected from one side of the main body portion 31, and a flange portion 33. The diameter of the main body 31 is smaller than that of the main body 21 of the fixed scroll 20. The spiral wall 32 is erected toward the fixed scroll 20, and is provided at a position where it is engaged with the spiral wall 22 of the fixed scroll 20. Thus, a plurality of spiral compression chambers 80 surrounded by the spiral wall bodies 22 and 32 and the main body portions 21 and 31 are formed between the fixed scroll 20 and the movable scroll 30. The flange portion 33 has an annular shape, and is integrally formed with the main body portion 31 on the surface opposite to the surface on which the spiral wall body 32 is provided.

  A suction pipe connection port 11 is formed in the housing 10, and the suction pipe connection port 11 communicates with the outer peripheral portion of the compression chamber 80 in the housing 10. The shaft 40 includes a large diameter portion 41, and includes an eccentric pin 42 at the tip of the large diameter portion 41. The eccentric pin 42 is provided at a position that is eccentric with respect to the axis of the shaft 40 (referred to as a compressor shaft). The eccentric pin 42 is connected to the flange portion 33 via an eccentric bush 43 and a bearing 44. The large-diameter portion 41 of the shaft 40 is rotatably supported by the housing 10 via a bearing 45. A base end portion 46 of the shaft 40 is fixed to the clutch pulley 50. The clutch pulley 50 is rotatably supported by the housing 10 via a bearing 51. The clutch pulley 50 receives the driving force of the gas engine 400 (see FIG. 8) via the belt, and rotates the shaft 40 by this driving force. On the outer periphery of the shaft 40, a mechanical seal 47 is provided between the base end portion 46 and the large diameter portion 41 and the housing 10.

  As the shaft 40 rotates, the movable scroll 30 rotates about a position eccentric from the rotation axis of the shaft 40 by a predetermined amount. In this case, the movable scroll 30 performs a turning motion because rotation is prevented by an Oldham coupling (not shown). By this orbiting motion, the plurality of spiral compression chambers 80 formed between the spiral wall body 22 of the fixed scroll 20 and the spiral wall body 32 of the movable scroll 30 are gradually reduced in volume while rotating. The fixed scroll 20 moves from the outer peripheral side to the center. The compression chamber 80 communicates with the discharge port 61 when guided to the center of the fixed scroll 20. The compression chamber 80 communicates with the relief port 62, the reduce port 63, the heating injection port 71, and the cooling injection port 72 in accordance with the moving position in the process of moving from the outer peripheral side of the fixed scroll 20 to the central portion. .

  When the orbiting scroll 30 turns, the refrigerant is sucked from the outer peripheral side of the fitting portion between the fixed scroll 20 and the orbiting scroll 30 and introduced into the compression chamber 80. Then, the refrigerant is compressed due to a decrease in the volume of the compression chamber 80 accompanying the turning motion of the movable scroll 30, and is discharged from the discharge port 61 at a high pressure. Further, the refrigerant amount in the compression chamber 80 is adjusted in the process until the compression chamber 80 communicates with the discharge port 61 by the operation of a valve mechanism described later. For example, the refrigerant is configured to escape from the relief port 62 when the compression chamber 80 is in an overpressure state during compression. Further, when the load required for air conditioning is high and a high load operation is performed, a refrigerant having an intermediate pressure is injected into the compression chamber 80 from the heating injection port 71 or the cooling injection port 72 during the compression. Further, when the air-conditioning demand load is low and the low-load operation is performed, the refrigerant is discharged from the reduce port 63 during the compression.

  Hereinafter, the valve mechanism for adjusting the flow rate of the refrigerant will be described with reference to FIGS. 3 represents a cross section orthogonal to the compressor axis at the AA cutting line of FIG. 1, FIG. 6 represents a cross section orthogonal to the compressor axis at the BB cutting line of FIG. 1, and FIG. FIG. 7 is a layout diagram showing the layout of each part by combining FIGS. 3 and 6. In addition, about the valve mechanism shown in FIG. 1, the cross section along the compressor axial direction in the XX cutting | disconnection line of FIG. 7 is represented. In the housing 10, a first heating reed valve unit 90 a and a second heating injection reed valve are provided on the back surface side (the side where the spiral wall body 22 is not formed) of the main body 21 of the fixed scroll 20. A unit 90b, a first cooling reed valve unit 90c, and a second cooling reed valve unit 90d are provided. FIG. 3 shows the positions of the injection reed valve units 90a to 90d and the positions of the injection ports 71a, 71b, 72a, 72b provided on the fixed scroll 20, using a cross section orthogonal to the compressor axis of the housing 10. Represents a relationship. The first heating reed valve unit 90a is provided at a position extending in the axial direction from the first heating injection port 71a formed in the fixed scroll 20, and the second heating reed valve unit 90b is The first cooling reed valve unit 90c is provided at a position extending in the axial direction from the second heating injection port 71b, and is provided at a position extended in the axial direction from the first cooling injection port 72a. The cooling reed valve unit 90d is provided at a position extending in the axial direction from the second cooling injection port 72b. In FIG. 1, as an example, a first heating reed valve unit 90a is shown. Each reed valve unit 90a, 90b, 90c, 90d has the same configuration. Therefore, when it is not necessary to distinguish these, each reed valve unit 90a, 90b, 90c, 90d is simply called the reed valve unit 90 for injection.

  As shown in FIG. 4, the injection reed valve unit 90 includes a casing 91, a retainer 92 provided in the casing 91, and a reed valve main body 93. The casing 91 is formed in a square box shape, and an inner surface of one of them is a seating surface 94 on which the reed valve main body 93 is seated. The seating surface 94 is formed with an inlet opening 95 serving as an inlet through which an intermediate-pressure injection refrigerant is introduced. The inlet opening 95 is formed at a position facing the tip side of the reed valve main body 93. The retainer 92 is formed with an inclined holding surface 96 that receives and holds the back surface of the reed valve body 93 when the reed valve body 93 is opened. The inclined holding surface 96 is inclined and faces the seating surface 94 formed on the casing 91, and is curved so as to slightly bulge toward the seating surface 94. One end of the inclined holding surface 96 is formed as a flat surface parallel to the seating surface 94.

  The reed valve main body 93 is a thin metal plate having a spring property, and is fastened with a screw S in a state where one end in the longitudinal direction is sandwiched between the seating surface 94 and the flat surface of the retainer 92. The surface 94 and the retainer 92 are clamped and fixed. The other end of the reed valve body 93 is a free end. In this way, the reed valve main body 93 is arranged in parallel to the seating surface 94 by fixing one end thereof to the seating surface 94, and the free end closes the inlet opening 95. All the surfaces of the retainer 92 except the inclined holding surface 96 are closely fixed to the inner side surface of the casing 91 so that the injection refrigerant cannot flow into the side surface side and the back surface side of the inclined holding surface 96. A space having a substantially sectoral cross section formed between the seating surface 94 and the inclined holding surface 96 of the retainer 92 is a space in which the reed valve main body 93 is opened and closed, and a space through which the injection refrigerant can pass. This space is called a valve chamber 97. FIG. 5 is a perspective view for explaining the shape of the valve chamber 97. In the present embodiment, in order to make the volume of the valve chamber 97 as small as possible, the sizes of the retainer 92 and the casing 91 are set in accordance with the width direction dimension and the longitudinal direction dimension of the reed valve main body 93. That is, the dimensions of the retainer 92 and the casing 91 are set so that the internal volume becomes as small as possible within a range that does not disturb the opening / closing operation of the reed valve main body 93.

  In the casing 91, an outlet opening 98 for sending the injection refrigerant is formed on a surface facing the valve chamber 97 and perpendicular to the seating surface 94 on the free end side of the reed valve main body 93. A surface on which the outlet opening 98 is formed is referred to as an outlet surface 99. Therefore, the outlet surface 99 and the outlet opening 98 are formed in the direction from the fixed end of the reed valve main body 93 to the free end with respect to the reed valve main body 93.

  The reed valve unit 90 for injection is arranged so that the free end of the reed valve main body 93 is on the compression chamber 80 side, and the direction connecting the fixed end and the free end of the reed valve main body 93 is parallel to the compressor shaft. Is done. Accordingly, the inlet opening 95 faces in a direction orthogonal to the axial direction. The outlet opening 98 is directed in the axial direction, and sends out the injection refrigerant in the axial direction (direction from the fixed end of the reed valve main body 93 toward the free end).

  On the outer periphery of the housing 10, a heating injection pipe connection port 14 and a cooling injection pipe connection port 15 are provided. In the housing 10, an upstream heating injection passage 16 that connects the heating injection pipe connection port 14 and the inlet openings 95 of the two heating reed valve units 90 a and 90 b is formed. Further, an upstream cooling injection passage 17 is formed in the housing 10 so as to connect the cooling injection pipe connection port 15 and the inlet openings 95 of the two cooling reed valve units 90c and 90d. The upstream heating injection passage 16 and the upstream cooling injection passage 17 are formed in parallel with the surface orthogonal to the compressor shaft, and communicate with the inlet opening 95 so as to be orthogonal to the seating surface 94. The upstream cooling injection passage 17 is formed to be bent so that its axial position is shifted in the middle so as not to interfere with the upstream heating injection passage 16.

  In addition, a first heating injection passage 18a is formed in the housing 10 to communicate the outlet opening 98 of the first heating reed valve unit 90a and the first heating injection port 71a in a straight line. A second heating injection passage 18b is formed that connects the outlet opening 98 of the heating reed valve unit 90b and the second heating injection port 71b in a straight line. Further, a first cooling injection passage 19a is formed in the housing 10 to communicate the outlet opening 98 of the first cooling reed valve unit 90c and the first cooling injection port 72a in a straight line, and the second cooling is performed. A second cooling injection passage 19b is formed which communicates the outlet opening 98 of the hour injection reed valve unit 90d and the second cooling injection port 72b in a straight line. Therefore, each injection passage 18a, 18b, 19a, 19b is provided in parallel to the axial direction.

  A heating injection pipe 207 is connected to the heating injection pipe connection port 14, and a cooling injection pipe 206 is connected to the cooling injection pipe connection port 15.

  An intermediate-pressure injection refrigerant is selectively supplied from the outside to the heating injection pipe connection port 14 and the cooling injection pipe connection port 15. Thus, when the pressure in the compression chamber 80 communicating with the injection port 70 is lower than the intermediate pressure of the injection refrigerant, the reed valve main body 93 opens the valve due to the differential pressure, An injection refrigerant is injected into the compression chamber 80.

  In injecting the injection refrigerant, the reed valve unit 90 for injection is set by setting the orientation of the reed valve body 93 in the reed valve unit 90 for injection and the positional relationship between the inlet opening 95 and the outlet opening 98 as described above. The injection refrigerant can be passed through the shortest route. In this case, as shown by the arrows in FIGS. 4 and 5, the injection refrigerant introduced from the inlet opening 95 is guided to the surface of the reed valve main body 93 and changes its direction to the direction of the outlet opening 98. It flows out from the outlet opening 98 as it is. Accordingly, the shape of the passage of the injection refrigerant in the injection reed valve unit 90 is simplified, and a sufficient passage area can be secured while reducing the volume of the valve chamber 97 as much as possible. Thereby, there is little channel resistance and it can make a recompression volume small.

  In this embodiment, the injection reed valve unit 90 is incorporated in the housing 10 of the compressor 1, but instead, for example, the housing 10 is processed to form the valve chamber 97, The reed valve main body 93 may be attached to the valve chamber 97. Further, in the present embodiment, the retainer 92 is incorporated in the rectangular casing 91, but instead, for example, a casing having an inclined holding surface 96 may be formed. That is, you may make it use the casing (casing which the bottom face became the inclination holding surface) which shaved the shape of the retainer 92. FIG.

  As shown in FIG. 6, the housing 10 is formed with a first valve chamber 101 and a second valve chamber 102 which are airtightly partitioned. The first valve chamber 101 and the second valve chamber 102 are provided with seating surfaces 104 and 105 that are surfaces orthogonal to the compressor shaft, respectively.

  The seating surface 104 of the first valve chamber 101 has a discharge port 61 formed in the fixed scroll 20 and discharge ports 111 and relief holes 112a and 112b formed to communicate with the relief ports 62a and 62b in a straight line. The tip is open. In addition, the seating surface 105 of the second valve chamber 102 has tips of reduce holes 113a and 113b formed so as to communicate with the reduce ports 63a and 63b formed in the fixed scroll 20 in a straight line. . The first valve chamber 101 is provided with a discharge valve 121 that is a check valve for opening and closing the discharge hole 111 and relief valves 122a and 122b that are check valves for opening and closing the relief holes 112a and 112b. . The second valve chamber 102 is provided with reduce valves 123a and 123b which are check valves for opening and closing the reduce holes 113a and 113b.

  The discharge valve 121, the relief valves 122a and 122b, and the reduce valves 123a and 123b are reed valves, and are fixed by screws S in a state where one end thereof is sandwiched between the seating surfaces 104 and 105 by the retainer 124. The discharge valve 121 is provided so as to cover the discharge hole 111 at its tip (free end), the relief valves 122a and 122b are provided so as to cover the relief holes 112a and 112b at its tip, and the reduce valves 123a and 123b are provided. The tip is provided so as to cover the reduction holes 113a and 113b. Each reed valve is provided with a plate surface in a direction orthogonal to the compressor shaft. As shown in FIG. 1, each retainer 124 is formed as a plate having a curved surface shape inclined with respect to the seating surfaces 104 and 105, and holds the back surface of the reed valve while the reed valve is open. In FIG. 6, the retainer 124 is not shown to show the reed valve.

  As shown in FIG. 1, a discharge pipe connection port 12 and a reduce pipe connection port 13 are formed in the housing 10. In the housing 10, a discharge passage 131 that connects the discharge pipe connection port 12 and the first valve chamber 101, and a reduction passage 132 that connects the reduce pipe connection port 13 and the second valve chamber 102 are formed. .

  FIG. 7 is an arrangement view showing the arrangement of each part of the valve mechanism described above as seen from the axial direction. In the drawing, the configuration related to the injection reed valve unit 90 is shown by a solid line, and the configuration related to the other reed valves 121, 122a, 122b, 123a, 123b is shown by a broken line. As illustrated, all the injection reed valve units 90 and the injection passages 18a, 18b, 19a, 19b are arranged so as not to interfere with the first valve chamber 101 and the second valve chamber 102. Further, the upstream heating injection passage 16 and the upstream cooling injection passage 17 are displaced in the axial direction with respect to the first valve chamber 101 and the second valve chamber 102. There is no interference with the first valve chamber 101 and the second valve chamber 102.

  In the compressor 1 configured as described above, when the movable scroll 30 makes a swiveling motion, the compression chamber 80 formed in a spiral shape turns to gradually decrease the volume while turning to move from the outer peripheral side of the fixed scroll 20 to the central portion. Moving. When the compression chamber 80 communicates with the discharge port 61, the discharge valve 121 is opened by the pressure of the compressed refrigerant, and the refrigerant flows into the first valve chamber 101 and is discharged from the discharge pipe connection port 12. Thereby, a refrigerant | coolant is supplied to the refrigerant circuit of an air conditioner.

  If the pressure in the compression chamber 80 becomes excessively high before the compression chamber 80 communicates with the discharge port 61, the refrigerant pressure is reduced when the compression chamber 80 communicates with the relief port 62 a (62 b). As a result, the relief valve 122a (122b) is opened, and the refrigerant flows into the first valve chamber 101 and is discharged from the discharge pipe connection port 12.

  Further, when the air conditioner performs a low load operation, a reduction on-off valve 216 provided in a reduction pipe 215 described later is opened. In this case, before the compression chamber 80 communicates with the discharge port 61, and when the compression chamber 80 communicates with the reduce port 63a (63b), the reduce valve 123a (123b) is opened by the pressure of the refrigerant, and the refrigerant is supplied to the second valve. It flows into the chamber 102 and is discharged from the reduced piping connection port 13. The reduce pipe 215 is connected to the suction pipe 205 as will be described later. Therefore, it is possible to reduce the load on the compressor 1 by returning an excessive amount of refrigerant to the suction path with respect to the air conditioning load, thereby reducing the refrigerant flow rate per unit time supplied to the refrigerant circuit of the air conditioner.

  Here, the refrigerant circuit of the air conditioner will be described with reference to FIG. The air conditioner includes the above-described compressor 1 for compressing the gas refrigerant, indoor heat exchangers 221A and 221B for exchanging heat with the indoor air that is installed indoors, and the refrigerant that is installed outside the outdoor air. The outdoor heat exchanger 222 for heat exchange, the heating expansion valve 223A and the cooling expansion valve 223B for expanding the refrigerant, the four-way switching valve 210, the first gas-liquid separator 225 for separating the refrigerant into gas and liquid, and the first A two-gas-liquid separator 226, a sub heat exchanger 227 for exchanging heat between the refrigerant and the engine cooling water, a control device 300, and a gas engine 400 are provided.

  A discharge pipe connection port 12 of the compressor 1 is connected to a four-way switching valve 210 via a first pipe 201 which is a discharge pipe. The four-way switching valve 210 has four ports (a first port 211, a second port 212, a third port 213, and a fourth port 214). The four-way switching valve 210 includes a heating connection state in which the first port 211 is connected to the second port 212 and the third port 213 is connected to the fourth port 214, the first port 211 is connected to the third port 213, and The second port 212 is configured to be switched to a cooling connection state in which the second port 212 is connected to the fourth port 214. The first pipe 201 described above is connected to the first port 211 of the four-way switching valve 210. One end of the second pipe 202 is connected to the second port 212. One end of the third pipe 203 is connected to the third port 213, and one end of the fourth pipe 204 is connected to the fourth port 214.

  The other end side of the second pipe 202 is branched, and the indoor heat exchanger 221A is connected to one branch pipe, and the indoor heat exchanger 221B is connected to the other branch pipe. Each branch pipe is provided with a flow control valve 220A, 220B. The number of indoor heat exchangers may be one or three or more. An outdoor heat exchanger 222 is connected to the other end of the third pipe 203. Indoor heat exchangers 221A and 221B and outdoor heat exchanger 222 are connected by an intermediate pipe 256. The indoor heat exchangers 221A and 221B allow the refrigerant to flow into the interior from the second pipe 202 or the intermediate pipe 256, and exchange heat between the refrigerant that has flowed in and the room air. The outdoor heat exchanger 222 allows the refrigerant to flow into the inside from the intermediate pipe 256 or the third pipe 203, and allows the refrigerant and the outside air to exchange heat.

  The intermediate pipe 256 includes a heating intermediate pipe 256A and a cooling intermediate pipe 256B that branch at a point C in FIG. 8 and merge at a point D when viewed from the direction toward the outdoor heat exchanger 222 from the indoor heat exchangers 221A and 221B. Have. A heating check valve 291 and a heating expansion valve 223A are interposed in the heating intermediate pipe 256A. The heating check valve 291 allows the flow of the refrigerant in the heating intermediate pipe 256A from the point C to the point D and blocks the flow in the opposite direction. The heating expansion valve 223A expands the refrigerant passing therethrough.

  A cooling check valve 292, a pressure reducing valve 293, a second gas-liquid separator 226, and a cooling expansion valve 223B are interposed in the cooling intermediate pipe 256B. The cooling check valve 292 allows the refrigerant in the cooling intermediate pipe 256B from point D to point C to flow and blocks the flow in the opposite direction. The pressure reducing valve 293 depressurizes the refrigerant flowing through the cooling intermediate pipe 256B. The second gas-liquid separator 226 gas-liquid separates the refrigerant flowing through the cooling intermediate pipe 256B, flows the gas refrigerant to the cooling injection pipe 206, which will be described later, and flows only the liquid refrigerant to the cooling intermediate pipe 256B. The cooling expansion valve 223B expands the refrigerant passing therethrough.

  In addition, a heating injection pipe is provided in the middle part of the heating intermediate pipe 256A between the part where the heating expansion valve 223A is interposed and the part where the heating check valve 291 is interposed. One end of 207 communicates. The other end of the heating injection pipe 207 is connected to the heating injection pipe connection port 14 of the compressor 1. A sub heat exchanger 227 is provided in the middle of the heating injection pipe 207. The refrigerant flowing through the heating injection pipe 207 flows into the sub heat exchanger 227. The refrigerant flowing into the sub heat exchanger 227 exchanges heat with the cooling water that has cooled the gas engine 400. The sub heat exchanger 227 evaporates liquid refrigerant out of the refrigerant flowing through the heating injection pipe 207. Further, the heating injection pipe 207 is provided with a heating injection on-off valve 208 on the upstream side of the sub heat exchanger 227.

  Further, one end of the cooling injection pipe 206 communicates with the second gas-liquid separator 226. The other end of the cooling injection pipe 206 is connected to the cooling injection pipe connection port 15 of the compressor 1. A cooling injection on / off valve 209 is provided in the middle of the cooling injection pipe 206.

  The other end of the fourth pipe 204 is connected to the first gas-liquid separator 225. The first gas-liquid separator 225 performs gas-liquid separation of the refrigerant that has flowed there. One end of a fifth pipe 205 that is a suction pipe communicates with the first gas-liquid separator 225. The other end of the fifth pipe 205 is connected to the suction pipe connection port 11 of the compressor 1. The gas refrigerant out of the refrigerant gas-liquid separated by the first gas-liquid separator 225 flows through the fifth pipe 205 and is supplied to the compressor 1.

  Further, one end of the reduce pipe 215 is connected to the reduce pipe connecting port 13 of the compressor 1. The other end of the reduce pipe 215 is connected to the fifth pipe 205. A reduction opening / closing valve 216 is provided in the middle of the reduction pipe 215.

  Next, the air conditioning operation (heating operation, cooling operation) of this air conditioner will be described. The operation control of the air conditioner is performed by the control device 300. Since this operation control is not a feature of the present invention, it will be briefly described below. First, the heating operation will be described. During the heating operation, the four-way selector valve 210 is brought into a heating connection state. When the compressor 1 is activated during the heating operation, the high-pressure gas refrigerant compressed by the compressor 1 is discharged to the first pipe 201 (discharge pipe). The high-pressure gas refrigerant discharged to the first pipe 201 enters the four-way switching valve 210 from the first port 211, is sent to the second pipe 201, and flows into the indoor heat exchangers 221A and 221B. The high-pressure gas refrigerant that has flowed into the indoor heat exchangers 221A and 221B is condensed by discharging heat to the indoor air while flowing through the indoor heat exchangers 221A and 221B. At this time, the indoor air is warmed by the heat discharged from the high-pressure gas refrigerant, and the room is heated.

  Refrigerant condensed by exhausting heat to the indoor air is partially liquefied and flows out of the indoor heat exchangers 221A and 221B, flows through the intermediate pipe 256, and further flows into the heating intermediate pipe 256A from the position indicated by the point C. Then, the pressure is reduced so as to be easily evaporated by being expanded by the heating expansion valve 223A, and then flows into the outdoor heat exchanger 222. The refrigerant flowing into the outdoor heat exchanger 222 takes the heat of the outside air and evaporates while flowing through the outdoor heat exchanger 222.

  A part of the refrigerant evaporated by taking the heat of the outside air is vaporized and flows out of the outdoor heat exchanger 222 and flows through the third pipe 203. Then, it enters the four-way switching valve 210 from the third port 213, is sent to the fourth pipe 204, and flows into the first gas-liquid separator 225. In the first gas-liquid separator 225, the refrigerant is separated into a liquid refrigerant and a low-pressure gas refrigerant. Then, only the low-pressure gas refrigerant flows through the fifth pipe 205 (suction pipe) and returns to the compressor 1.

  Next, the cooling operation will be described. During the cooling operation, the four-way switching valve 210 is brought into a cooling connection state. When the compressor 1 is activated during the cooling operation, the high-pressure gas refrigerant compressed by the compressor 1 is discharged to the first pipe 201. The high-pressure gas refrigerant discharged to the first pipe 201 enters the four-way switching valve 210 from the first port 211, is sent to the third port 213, and flows into the outdoor heat exchanger 222. The high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 222 is condensed while discharging heat to the outside air while flowing through the outdoor heat exchanger 222.

  The refrigerant condensed by exhausting heat to the outside air is partially liquefied and flows out of the outdoor heat exchanger 222 and flows through the intermediate pipe 256, flows into the cooling intermediate pipe 256B from the position indicated by the point D, and is reduced by the pressure reducing valve 293. After being depressurized, it flows into the second gas-liquid separator 226. The second gas-liquid separator 226 separates the refrigerant into a gas refrigerant and a liquid refrigerant. Of the separated refrigerant, only the liquid refrigerant further flows through the cooling intermediate pipe 256B. Then, the pressure is reduced so as to be easily evaporated by being expanded by the cooling expansion valve 223B, and then flows into the indoor heat exchangers 221A and 221B. The refrigerant flowing into the indoor heat exchangers 221A and 221B evaporates by taking the heat of the indoor air while flowing through the indoor heat exchangers 221A and 221B. At this time, the refrigerant takes the heat of the room air, thereby cooling the room air and cooling the room.

  The refrigerant that has evaporated the heat of the indoor air is partially vaporized, flows out of the indoor heat exchangers 221A and 221B, and flows through the second pipe 202. Then, it enters the four-way switching valve 210 from the second port 212, is sent to the fourth pipe 204, and flows into the first gas-liquid separator 225. In the first gas-liquid separator 225, the refrigerant is separated into a liquid refrigerant and a low-pressure gas refrigerant. Then, only the low-pressure gas refrigerant flows through the fifth pipe 205 and returns to the compressor 1.

  Thus, during heating, the indoor heat exchangers 221A and 221B serve as condensers and the outdoor heat exchanger 222 serves as an evaporator. On the other hand, during cooling, the outdoor heat exchanger 222 becomes a condenser and the indoor heat exchangers 221A and 221B become evaporators.

  When the required air conditioning load of the air conditioner is high, a high load operation is performed. When a high load operation is performed, the heating injection on / off valve 208 is maintained in the open state during the heating operation, and the cooling injection on / off valve 209 is maintained in the open state during the cooling operation. Is done. These on-off valves 208 and 209 are maintained in a closed state when the valve opening state is controlled by the control device 300 and high load operation is not performed.

  During high-load operation, during heating operation, each inlet opening 95 of the first heating reed valve unit 90a and second heating reed valve unit 90b is in communication with the intermediate pipe 256A. . In this case, since the refrigerant in the intermediate pipe 256A has an intermediate pressure, when the compression chamber 80 communicates with the first heating injection port 71a and the second heating injection port 71b, the first heating-use reed valve unit 90a. The second heating reed valve unit 90b is opened by the differential pressure and flows into the compression chamber 80. In the cooling operation, the inlet openings 95 of the first cooling reed valve unit 90c and the second cooling reed valve unit 90d and the intermediate pipe 256B are in communication with each other. In this case, since the refrigerant in the intermediate pipe 256B has an intermediate pressure, when the compression chamber 80 communicates with the first cooling injection port 72a and the second cooling injection port 72b, the first cooling reed valve unit 90c. The second cooling reed valve unit 90d is opened by the differential pressure and flows into the compression chamber 80. Thereby, at the time of high load operation, the refrigerant | coolant flow volume per unit time supplied to the refrigerant circuit of an air conditioner can be increased, and a high air-conditioning request | requirement load can be coped with.

  When the air conditioning requirement load of the air conditioner is low, low load operation is performed. The control device 300 maintains the reducing on-off valve 216 in an open state only when performing a low load operation. Thereby, the 2nd valve chamber 102 and the 5th piping 205 will be in a communication state. Therefore, when the compression chamber 80 communicates with the reduce port 63a (63b), the reduce valve 123a (123b) is opened by the pressure of the refrigerant in the compression chamber 80, and the refrigerant in the compression chamber 80 is It returns to the 5th piping 205 via the chamber 102 and the reduction piping 215. Therefore, an excessive amount of refrigerant can be returned to the suction path with respect to the air conditioning load, the refrigerant flow rate per unit time supplied to the refrigerant circuit of the air conditioner can be reduced, and a low air conditioning requirement load can be dealt with. .

  When the required air conditioning load of the air conditioner is in an intermediate range, normal load operation is performed. When performing normal load operation, the control device 300 maintains the injection on / off valves 208 and 209 and the reducing on / off valve 216 in a closed state, and adjusts the refrigerant flow rate by controlling the rotational speed of the gas engine 400.

According to the compressor 1 of the present embodiment described above, the injection reed valve unit 90 is provided in the passage for injecting the intermediate-pressure gas refrigerant into the compression chamber 80, and the following effects are obtained.
1. The reed valve unit 90 for injection is arranged so that the free end of the reed valve main body 93 is on the compression chamber 80 side, and the direction connecting the fixed end and the free end of the reed valve main body 93 is parallel to the compressor shaft. In addition, the outlet surface 99 and the outlet opening 98 are formed in a direction from the fixed end of the reed valve main body 93 toward the free end. In addition, a valve chamber 97 is formed on the back surface and side surface of the retainer 92 so that there is no space into which the injection refrigerant can flow. Accordingly, the inlet opening 95 and the outlet opening 98 are provided at positions close to each other, the distance through which the injection refrigerant passes through the valve chamber 97 can be shortened, and the shape of the passage can be simplified. Thereby, it is possible to secure a sufficient passage area while making the volume of the valve chamber 97 as small as possible. As a result, the flow resistance is small, the recompression volume can be reduced, and the compression efficiency of the compressor 1 can be improved.

2. The compressor 1 includes a large number of reed valves (injection reed valve × 4, discharge valve × 1, relief valve × 2, reduce valve × 2), but the plate surface of the reed valve for injection is compressed. It arrange | positions so that it may become parallel to a machine shaft, and about the other reed valve, the plate | board surface is arrange | positioned toward the direction orthogonal to a compressor shaft. Therefore, when a plurality of reed valves having a plurality of functions are provided in a mixed manner, the layout of the reed valves is facilitated. For example, when all nine reed valves used in the present embodiment are arranged so that the plate surface is in a direction orthogonal to the compressor shaft, the area occupied by the plate surface of the reed valve, the occupation of the valve chamber Since the area to be processed increases, their layout is difficult. On the other hand, in this embodiment, as shown in FIG. 7, in order to combine the direction of the plate surface of the reed valve provided parallel to the compressor shaft and the direction directed to the direction orthogonal to the compressor shaft. It is possible to cope with an increase in reed valves.

  The refrigerant compressor of this embodiment has been described above, but the present invention is not limited to the above embodiment, and various modifications can be made without departing from the object of the present invention.

  For example, in the present embodiment, four injection reed valves are provided, but the number of injection reed valves can be arbitrarily set. Similarly, the number of other reed valves can be arbitrarily set.

  DESCRIPTION OF SYMBOLS 1 ... Compressor, 10 ... Housing, 20 ... Fixed scroll, 22 ... Spiral wall body, 30 ... Movable scroll, 32 ... Spiral wall body, 40 ... Shaft, 61 ... Discharge port, 62a, 62b ... Relief port, 63a , 63b ... Reduce port, 71a, 71b ... Heating injection port, 72a, 72b ... Cooling injection port, 80 ... Compression chamber, 90 ... Reed valve unit for injection, 90a, 90b ... Reed valve unit for heating injection, 90c , 90d ... Reed valve unit for cooling injection, 91 ... Casing, 92 ... Retainer, 93 ... Reed valve body, 94 ... Seating surface, 95 ... Inlet opening, 96 ... Inclined holding surface, 97 ... Valve chamber, 98 ... Outlet opening , 99 ... Outlet surface, 206 ... Injection pipe for cooling, 207 ... Warm Use injection pipe, 215 ... Reduce piping.

Claims (1)

A housing;
A fixed scroll fixed in the housing and formed with a spiral wall;
A movable scroll having a spiral wall formed therein and revolving with respect to the fixed scroll in the housing;
A compression chamber that is formed between the spiral wall of the fixed scroll and the spiral wall of the movable scroll and compresses and discharges the low-pressure refrigerant sucked by the orbiting motion of the movable scroll;
An injection port for introducing an intermediate pressure refrigerant into the compression chamber in a refrigerant circuit through which the refrigerant discharged from the compression chamber flows;
In a refrigerant compressor provided with a reed valve portion that functions as a check valve and that is provided in an introduction path for introducing refrigerant into an injection port,
The reed valve portion includes a plate-shaped reed valve body having one end as a fixed end and the other end as a free end, a retainer that holds the back surface of the reed valve body when the reed valve body is opened, An inlet is formed and the reed valve main body is seated when the valve is closed to cover the inlet, and a valve chamber formed between the seating surface and the retainer and serving as a movable space of the reed valve main body,
The reed valve body is arranged such that the free end is closer to the compression chamber than the fixed end, and the direction connecting the fixed end and the free end is parallel to the compressor shaft ,
An introduction path communicating with the inlet is formed in parallel with a plane orthogonal to the compressor shaft;
The refrigerant compressor according to claim 1, wherein an outlet for sending the refrigerant to the injection port is formed in the valve chamber in a direction from the fixed end to the free end of the reed valve main body.

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