JP2006177183A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor capable of minimizing increase in bearing load of each part and leakage loss in a compression chamber even if injection is performed. <P>SOLUTION: This scroll compressor is provided with an injection path provided in a base plate back face part of a fixed scroll and connected with a closed vessel; an injection port passing through a base plate of the fixed scroll from the injection path and communicated with the compression chamber; an air bleed provided on a base plate of an oscillating scroll and leading out refrigerant gas pressurized in the compression chamber; and a communication path provided in a thrust bearing part of a compliant frame and arranged such that an only limited section of the communication path can be communicated with the air bleed every one rotation of a main shaft. A frame space blocked from inside of the closed vessel in terms of pressure is formed on the outside face of the compliant frame. A section in which the compression chamber is communicated with the frame space is set to be all the time within a space in which the injection port is communicated with the compression chamber. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a scroll compressor used in a refrigeration air conditioner or the like.

In the conventional scroll compressor, the suction refrigerant gas set by the heat exchanger is sucked into the compressor and compressed, and the high-temperature and high-pressure refrigerant gas is supplied to the external cycle. When it is low, the refrigerant circulation amount supplied to the external cycle is insufficient, and the capacity is insufficient.
JP-A-4-370383

  In the conventional scroll compressor, with the main purpose of cooling the compression mechanism, the refrigerant is injected into the compression chamber in the middle of compression (hereinafter referred to as injection) to improve performance and reliability. However, the fact that the refrigerant gas is introduced into the compression chamber in the middle of compression means that the relationship between the pressure Pm in the middle of compression and the injection pressure Pinj is Pm <Pinj, and the gas load due to the compression increases in both the radial direction and the axial direction. Become. For this reason, even if the injection gas having a low temperature is introduced into the compression chamber and the temperature of the compression mechanism can be cooled, the bearing load of each portion increases and the leakage loss of the compression chamber increases. When the leakage loss in the compression chamber increases, the refrigerant gas in the middle of compression is recompressed, which leads to further increase in loss, and thus does not lead to improvement in the reliability and efficiency of the compressor.

  The present invention has been made to solve the above-described problems, and has a scroll compressor mechanism that can suppress an increase in bearing load and compression chamber leakage loss to a minimum even when injection is performed. The purpose is to provide.

  A scroll compressor according to the present invention includes a compliant frame having a main bearing that supports a main shaft that drives a swing scroll by forming a compression chamber by meshing plate-like spiral teeth of a fixed scroll and a swing scroll. In a scroll compressor provided with a compression mechanism in an airtight container, it is provided on the back of the base plate of the fixed scroll and is connected to the compression chamber through the injection path connected from the airtight container and the base plate of the fixed scroll. An injection port, a oscillating scroll base plate, a bleed hole for leading the refrigerant gas pressurized in the compression chamber, and a thrust bearing portion of the compliant frame. Compliant with a communication path arranged so that only a limited section can communicate A frame space that is pressure-blocked with the inside of the sealed container is formed on the outer surface of the frame, and the section in which the compression chamber and the frame space communicate with each other is always in the section in which the injection port and the compression chamber communicate with each other. It is characterized by that.

  With the above configuration, the scroll compressor according to the present invention can minimize the increase in bearing load and leakage loss of the compression chamber even when injection is performed.

Embodiment 1 FIG.
1 to 11 are diagrams showing Embodiment 1, FIG. 1 is a diagram showing a refrigerant circuit provided with a scroll compressor, and FIG. 2 is a partial longitudinal sectional view for explaining the vicinity of a fixed scroll of the scroll compressor. 3 is a top view of the scroll compressor, FIG. 4 is a partial longitudinal sectional view for explaining the vicinity of the orbiting scroll of the scroll compressor, and FIG. 5 is a sectional view showing the positional relationship between the compression chamber, the injection port, and the bleed holes. 6 is a partial longitudinal sectional view for explaining the vicinity of the compliant frame of the scroll compressor, FIG. 7 is a partial longitudinal sectional view for explaining the vicinity of the guide frame of the scroll compressor, and FIG. 8 is a longitudinal sectional view of the scroll compressor. 9 is an enlarged view showing the trajectory of the end of the bleed hole of the scroll compressor, FIG. 10 is a schematic view showing the communication port of the injection port and the bleed hole of the scroll compressor, and FIG. During steady operation of Le compressor, a mechanical illustration during injection operation (steady operation) and injection during operation (abnormal operation).

  In FIG. 1, the refrigerant sucked from the suction pipe 10a (right side in FIG. 1) is compressed by the compressor, discharged from the discharge pipe 10b (lower left side in FIG. 1) to the refrigeration cycle, passes through the condenser 53, and is liquefied. The refrigerant thus depressurized through the decompressor 54 returns to the suction pipe 10a again through the evaporator 55. A part of the liquefied refrigerant can flow into the injection pipe 10c (upper left side in FIG. 1) through the flow control valve 51 and the injection refrigerant supply pipe 52.

  In FIG. 2, the outer periphery of the fixed scroll 1 is fastened to the guide frame 15 by bolts (not shown), and a plate-like spiral tooth 1b is formed below the fixed scroll base plate 1a. A pair of Oldham ring guide grooves 1c are formed substantially in a straight line, and two pairs of fixed side claws 9c of the Oldham ring 9 are engaged with the Oldham ring guide grooves 1c so as to be capable of reciprocating.

  Further, a suction pipe 10a and an injection pipe 10c are press-fitted through the sealed container 10 in the side direction of the fixed scroll 1, and are connected to the injection pipe 10c and fastened to the upper surface of the fixed scroll base plate 1a with bolts (not shown). An injection path 60a provided in the injection plate 60 formed is formed and connected to an injection port 1h provided in the fixed scroll base plate 1a. The injection plate 60 is installed in a form in which metal surfaces are joined to the back surface of the fixed scroll base plate 1a of the fixed scroll 1 (see also FIG. 3).

  In FIG. 4, the orbiting scroll 2 is formed with plate-like spiral teeth 2b having substantially the same shape as the plate-like spiral teeth 1b of the fixed scroll 1 on the upper side of the orbiting scroll base plate 2a. A pair of compression chambers are formed continuously in combination with the teeth 1b, and an injection port 1h connected from the injection path 60a communicates with each compression chamber.

  Here, the arrangement position of the injection port is shown in FIG. The injection port 1h is disposed at a position communicating with the compression chamber 70 after the outermost compression chamber 70 formed by the combination of the plate-like spiral teeth 1b and 2b is formed.

  In FIG. 4, a hollow cylindrical boss 2f is formed at the center of the surface (lower side in FIG. 4) opposite to the plate-like spiral tooth 2b of the swing scroll base plate 2a. A rocking bearing 2c is formed on the inner peripheral surface of the portion 2f. In addition, a thrust surface 2d that can slide in pressure contact with the thrust bearing 3a of the compliant frame 3 is formed on the outer peripheral portion of the surface on the same side as the boss portion 2f.

  Further, on the outer peripheral portion of the swing scroll base plate 2a of the swing scroll 2, two pairs of Oldham ring guide grooves 2e having a phase difference of approximately 90 degrees with the Oldham ring guide groove 1c of the fixed scroll 1 are substantially aligned. In this Oldham ring guide groove 2e, two pairs of swinging side claws 9a of the Oldham ring 9 are engaged so as to freely reciprocate.

  Further, the swing scroll base plate 2a is a hole that communicates the surface on the fixed scroll 1 side (upper surface in FIG. 4) and the surface on the compliant frame 3 side (lower surface in FIG. 4). A bleed hole 2j is formed. The bleed hole opening 2k on the compliant frame side surface of the bleed hole 2j is arranged so that its circular locus always fits within the thrust bearing 3a of the compliant frame 3 during normal operation.

  In FIG. 6, a main bearing 3 c and an auxiliary bearing 3 h that support the main shaft 4 that is rotationally driven by an electric motor in the radial direction are formed at the center of the compliant frame 3. The compliant frame 3 is formed with a communication passage 3s that communicates with the frame space 15f from the surface of the thrust bearing 3a.

  The compliant frame 3 is also formed with a pressure regulating valve housing space 3p. One end of the pressure regulating valve housing space 3p communicates with the swinging scroll back pressure chamber 2h, and the other end is the outer space of the base plate. 2i.

  The pressure adjusting valve storage space 3p stores an intermediate pressure adjusting valve 3l that can freely reciprocate, and an intermediate pressure adjusting spring retainer 3t is fixedly stored on the compliant frame 3, and the intermediate pressure adjusting valve 3l. And intermediate pressure adjusting spring presser 3t, intermediate pressure adjusting spring 3m is retracted from its natural length and stored.

  In FIG. 7, the outer peripheral surface 15 g of the guide frame 15 is fixed to the sealed container 10 by shrink fitting or welding, but the high-pressure refrigerant gas discharged from the discharge port 1 f of the fixed scroll 1 is transferred from the guide frame 15 to the electric motor. A flow path leading to the discharge pipe 10b provided on the side (lower side in FIG. 7) is secured.

  Further, an upper fitting cylindrical surface 15 a is formed on the fixed scroll side (upper side in FIG. 7) of the inner side surface of the guide frame 15, and an upper fitting cylindrical surface 3 d formed on the outer peripheral surface of the compliant frame 3. Is engaged. On the other hand, a lower fitting cylindrical surface 15b is formed on the motor side (lower side in FIG. 7) of the inner side surface of the guide frame 15, and a lower fitting cylindrical surface 3e formed on the outer peripheral surface of the compliant frame 3; Is engaged.

  Further, two ring-shaped seal grooves for accommodating the seal material are formed on the inner side surface of the guide frame 15, and the ring-shaped upper seal material 16a and the ring-shaped lower seal material 16b are formed in these seal grooves. Is inserted. The space formed by these two sealing materials and the outer surface of the compliant frame 3 forms a frame space 15f.

  The ring-shaped groove that accommodates the upper seal material 16a and the lower seal material 16b may be on the outer peripheral side of the compliant frame 3.

  Further, the upper sealing material 16a and the lower sealing material 16b are not necessarily required, and are parts that can be omitted by performing sealing in a minute gap at an engagement location (for example, by forming an oil film).

  The guide frame 15 is also formed with a pressure regulating valve housing space 15p. One end of the pressure regulating valve housing space 15p communicates with the frame space 15f, and the other end is a discharge pressure space in the sealed container 10. Communicate. Further, in this pressure adjusting valve storage space 15p, an intermediate pressure adjusting valve 32 is stored so as to freely reciprocate, and an intermediate pressure adjusting valve presser 15t is fixedly stored on the guide frame 15, and these intermediate pressure adjusting valve 32 and Between the intermediate pressure adjusting spring presser 15t, an intermediate pressure adjusting spring 15m is retracted from its natural length and stored.

  The space on the outer peripheral side of the thrust bearing 3a surrounded by the oscillating scroll base plate 2a of the orbiting scroll 2 and the compliant frame 3, that is, the base plate outer peripheral space 2i, is near the end of winding of the plate-like spiral teeth. Since it communicates with a certain suction space 1g, it is a low pressure space with a suction gas atmosphere (suction pressure).

  In FIG. 8, an oscillating shaft portion 4 b that is rotatably engaged with the oscillating bearing 2 c of the oscillating scroll 2 is formed at the end of the oscillating scroll side (upper side in FIG. 8) of the main shaft 4. A spindle balancer 4e is shrink fitted on the lower side. Further, a main shaft portion 4c that is rotatably engaged with the main bearing 3c and the auxiliary bearing 3h of the compliant frame 3 is formed on the lower side thereof.

  Further, the other end portion of the main shaft 4 is formed with a sub shaft portion 4 d that is rotatably engaged with the sub bearing 6 a of the sub frame 6. An electric motor rotor 8 is shrink-fitted between the auxiliary shaft portion 4d and the main shaft portion 4c described above.

  Further, the lower end surface of the main shaft 4 is submerged in the refrigerating machine oil 10e accumulated at the bottom of the hermetic container 10, and the refrigerating machine oil 10e is supplied to each sliding portion through a main shaft through hole 4g provided in the main shaft 4.

Next, the operation will be described.
During the steady operation, the suction gas is sucked from the suction pipe 10a, and the refrigerant gas is sequentially compressed by the compression chamber 70 formed by the plate-like spiral teeth 1b, 2b of the fixed scroll 1 and the swing scroll 2. The refrigerant gas having an intermediate pressure during the compression process is guided to the frame space 15f through the extraction holes 2j formed in the swing scroll 2 and the communication passage 3s provided in the compliant frame 3. When the refrigerant gas is compressed in the compression chamber 70 formed by the plate-like spiral teeth 1b and 2b of the fixed scroll 1 and the swing scroll 2, the swing scroll 2 has a radial direction and a shaft along with the refrigerant gas compression. In response to the gas load in the direction (lower side in FIG. 2), the orbiting scroll 2 tends to move downward.

  On the other hand, the compliant frame 3 is pushed upward together with the orbiting scroll 2 by the intermediate pressure Pm guided to the frame space 15f, and the gap between the base plate bottom of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2; The operation is performed in an optimum state in which the gap between the plate-like spiral teeth 1b of the fixed scroll 1 and the bottom of the base plate of the swing scroll 2 is minimized.

  As described above, the pressure in the frame space 15f is guided from the compression chamber in the middle of compression. At this time, as shown in FIG. 9, the bleed hole 2j of the orbiting scroll 2 and the communication passage 3s of the compliant frame 3 are arranged so that they can communicate only in a limited section per one rotation of the main shaft 4. As shown in FIG. 9, the pressure fluctuation in the frame space 15f is set to be smaller than the pressure fluctuation in the compression chamber.

Next, the injection operation will be described.
At the time of the injection operation, the refrigerant having the intermediate pressure = Pinj passes through the injection pipe 10c press-fitted into the fixed scroll base plate 1a through the sealed container 10 and the injection path 60a provided in the injection plate 60, and is compressed with the pressure Pm. Guided to chamber 70. The pressure relationship at this time is Pm <Pinj.

  The injection refrigerant has a structure for guiding the refrigerant discharged from the compressor from the middle of the refrigeration circuit, and the temperature relationship at that time is Td> Tinj.

  As described above, since the injection operation increases the circulation amount of the discharged refrigerant by injecting refrigerant into the compression chamber 70 during compression, the injection port communicates with the compression chamber 70 immediately after the outermost compression chamber is formed. It is desirable. By performing the injection operation in this way, the refrigerant circulation amount increases, so that the performance of the refrigeration cycle is improved and the discharge gas temperature can be reduced.

  On the other hand, as shown in FIG. 11, when the injection operation is not performed (a), the pressure in the compression chamber 70 is guided to the frame space 15f through the extraction holes 2j, and the compliant frame 3 is pushed upward in the axial direction with an appropriate force Ff and fixed. Leakage of the compression chamber 70 by minimizing the gap between the bottom of the base plate of the scroll 1 and the plate-like spiral tooth 2b of the orbiting scroll 2 and the gap between the plate-like spiral tooth 1b of the fixed scroll 1 and the bottom of the base plate of the orbiting scroll 2. It is operated with the loss minimized.

  Next, in the case of steady operation at the time of injection (b), since the injection refrigerant satisfying Pm <Pinj is supplied to the compression chamber 70 in the middle of compression, the compression load increases, and the swing scroll 2 and the compliant frame are increased. 3 is pushed downward, and the fixed scroll 1 and the swing scroll 2 are separated. However, as can be seen from the relationship between the communication space between the frame space 15f and the compression chamber 70 shown in FIG. 10 and the communication timing between the injection path 60a and the compression chamber 70, the section where the compression chamber 70 and the frame space 15f communicate is always the injection path 60a. Therefore, the pressure Pminj in the frame space 15f at this time is Pm <Pminj <Pinj. Accordingly, when the pressure in the frame space 15f rises to Pminj, the force pushing up the orbiting scroll 2 and the compliant frame 3 increases to Ff1, and the base plate bottom of the fixed scroll 1 and the plate-like spiral teeth of the orbiting scroll 2 are increased. The operation is performed in a state in which the gap 2b and the gap between the plate-like spiral teeth 1b of the fixed scroll 1 and the bottom of the swing scroll 2 are minimized and the leakage loss of the compression chamber 70 is minimized. That is, it becomes possible to drive in the same state as during steady operation without injection.

  Further, when a refrigerant having a high pressure is suddenly injected into the compression chamber 70 through the injection pipe, or when a liquid (liquid refrigerant or refrigerating machine oil) that is an incompressible fluid is injected (c), the pressure in the compression chamber There is a risk of damaging the shafts, bearings, plate-like spiral teeth 1b, 2b, etc. due to sudden rise. However, when the above-described configuration is adopted, when the pressure in the compression chamber 70 is abnormally increased, the force Ff2 that pushes down the oscillating scroll 2 and the compliant frame 3 and the force Ff3 that pushes down the compliant frame 3 are Ff2 <Ff3. Therefore, the gap between the bottom of the base plate of the fixed scroll 1 and the plate-like spiral tooth 2b of the orbiting scroll 2 and the bottom of the base plate of the plate-like spiral tooth 1b of the fixed scroll 1 and the orbiting scroll 2 are as follows. It is possible to avoid damage to the bearing portion and the plate-like spiral teeth 1b and 2b by increasing the clearance of the pressure and releasing the pressure in the compression chamber 70.

  As described above, the refrigerant flow that circulates in the refrigeration circuit is increased by injecting the refrigerant at the intermediate pressure into the compression chamber 70 in the middle of compression, and the compressor efficiency is improved by minimizing the gap in the compression chamber 70. Therefore, it is possible to increase the heating capacity of the refrigeration cycle, and to avoid damage to the compressor by increasing the gap in the compression chamber 70 and reducing the pressure when the pressure in the compression chamber 70 increases abnormally. Is possible.

  Further, it is obvious that the same configuration and effect can be obtained even when the injection path 60a is provided in the fixed scroll base plate 1a of the fixed scroll 1.

  In the present embodiment, the injection plate 60 is described as being disposed directly on the back surface of the fixed scroll base plate 1a of the fixed scroll 1. However, the injection plate 60 is disposed between the back surface of the fixed scroll 1 and the fixed scroll base plate 1a. The same effect can be obtained even if the packing formed of a rubber material or the like is interposed between the injection plate 60 and the fixed scroll base plate 1a to improve the sealing performance.

Embodiment 2. FIG.
FIG. 12 shows the second embodiment, and is a longitudinal sectional view of a scroll compressor connected to a refrigerant circuit. In FIG. 12, the injection tube 10c communicates with an injection path 60a provided in an injection plate 60 installed on the back surface of the fixed scroll base plate 1a.

  In recent refrigeration cycle devices, the injection flow rate must be optimally matched to the operating state in accordance with the diversification of operation, so the injection refrigerant supply pipe 52 has a flow rate control that can adjust the flow rate according to the operation status. A valve 51 is provided. This control can be controlled by a microcomputer together with the operation control of the refrigeration circuit, for example, but is not limited to this control method.

  When the injection flow rate is controlled by such control, there may be a case where the injection flow rate and injection pressure set abnormally increase due to a transient situation, an abnormality of the control circuit, or the like. In this case, since the refrigerant with a high pressure is led to the compression chamber 70 in the middle of compression, the load required for the compression also increases rapidly, which may damage the shaft / bearing portion and the plate-like spiral teeth 1b and 2b. is assumed.

  However, as shown in FIG. 12, by making the injection path 60a provided in the fixed scroll 1 smaller in size than the inner diameter of the injection refrigerant supply pipe 52, pressure loss occurs in the injection path 60a and is led into the compression chamber. A rapid increase in the injection pressure can be mitigated, a rapid increase in the compression load can be suppressed, and a highly reliable injection scroll compressor can be obtained.

  Further, at the time of steady operation where injection operation is not performed, the section from the injection port 1h to the injection path 60a to the injection refrigerant supply pipe 52 to the injection flow rate control valve 51 becomes a dead volume, which degrades the single unit performance of the compressor. However, by reducing the flow path area of the injection path, it is possible to minimize the influence of dead volume during operation.

  In the present embodiment, the portion having a small flow path area has been described with the injection path 60a, but the same effect can be obtained as long as it is between the injection port 1h and the injection refrigerant supply pipe 52.

  Further, it is obvious that the same configuration and effect can be obtained even when the injection path 60a is provided in the fixed scroll base plate 1a of the fixed scroll 1.

Embodiment 3 FIG.
FIG. 13 shows the third embodiment, and is a partial longitudinal sectional view of a scroll compressor connected to the refrigerant circuit. In FIG. 13, an injection tube 10c and an injector 10f provided at the tip of the injection tube 10c are joined by welding or the like. The injector 10f is formed of a highly rigid member, and the inner diameter of the injector 10f is configured to be smaller than the inner diameter of the injection tube 10c.

  The injector 10f is press-fitted and connected to an injection path 60b provided in the fixed scroll base plate 1a, and communicates with an injection path 60a provided in an injection plate 60 installed on the back surface of the fixed scroll base plate 1a. Since the inner diameter of the injector 10f is configured to be small, the area that adversely affects the performance of the compressor alone as a dead volume is the volume between the injection port 1h and the injector 10f.

  In addition, since the injector 10f is made of a highly rigid member, the injector 10f can be hit with an air hammer or the like when the fixed scroll base plate 1a is press-fitted into the injection path 60b, and assembly is easy.

Embodiment 4 FIG.
FIG. 14 is a diagram illustrating the fourth embodiment, and is a diagram illustrating a refrigerant circuit including a scroll compressor. In FIG. 14, the injection tube 10c communicates with an injection path 60a provided in an injection plate 60 installed on the back surface of the fixed scroll base plate 1a (not shown). The injection connection pipe 80 connects the injection pipe 10c and the injection refrigerant supply pipe 52 in the refrigeration cycle, and is connected to the injection pipe 10c by welding or the like.

  The injection pipe 10c is disposed on the side surface of the sealed container 10, and the injection connection pipe 80 connected to the injection pipe 10c is partially curved until it is connected to the injection refrigerant supply pipe 52 in the refrigeration cycle. The injection connecting pipe bending portion 80a is provided so that the vibration and stress of the injection connecting pipe 80 can be absorbed.

  In recent years, refrigeration cycle equipment must be optimally adapted to the operating conditions as the operation flow diversifies, so depending on the operating conditions, the vibration of each pipe connected to the refrigeration cycle is large. As described above, it is possible to avoid problems such as broken pipes by providing the injection connection pipe 80 with a portion (injection connection pipe bending portion 80a) capable of absorbing vibration and stress as described above.

  In addition, the injection tube holder 10h provided in the sealed container 10 can improve the resistance to vibration and stress of the injection connection tube 80 by fixing the injection connection tube 80 and the injection tube holder 10h.

  If an impact absorbing material 10j made of a rubber material or the like is used between the injection connecting pipe 80 and the injection pipe holder 10h, it is possible to further improve the resistance to vibration and stress.

It is a figure which shows Embodiment 1, and is a figure which shows the refrigerant circuit provided with the scroll compressor. It is a figure which shows Embodiment 1, and is a fragmentary longitudinal cross-sectional view for demonstrating the fixed scroll vicinity of a scroll compressor. FIG. 3 is a diagram illustrating the first embodiment and is a top view of the scroll compressor. FIG. 5 is a diagram showing the first embodiment, and is a partial longitudinal sectional view for explaining the vicinity of an orbiting scroll of the scroll compressor. FIG. 5 shows the first embodiment, and is a cross-sectional view showing the positional relationship between the compression chamber, the injection port, and the extraction holes. FIG. 5 is a diagram showing the first embodiment, and is a partial longitudinal sectional view for explaining the vicinity of a compliant frame of the scroll compressor. FIG. 5 is a diagram showing the first embodiment, and is a partial longitudinal sectional view for explaining the vicinity of a guide frame of a scroll compressor. FIG. 5 is a diagram illustrating the first embodiment, and is a longitudinal sectional view of a scroll compressor. It is a figure which shows Embodiment 1, and is an enlarged view which shows the locus | trajectory of the bleed hole end part of a scroll compressor. It is a figure which shows Embodiment 1, and is a schematic diagram which shows the communication port of the injection port of a scroll compressor and an extraction hole. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Embodiment 1, and is a mechanical explanatory drawing at the time of the steady operation of a scroll compressor, the time of injection operation (at the time of steady operation), and the time of injection operation (at the time of abnormal operation). It is a figure which shows Embodiment 2, and is a longitudinal cross-sectional view of the scroll compressor connected to the refrigerant circuit. It is a figure which shows Embodiment 3, and is a fragmentary longitudinal cross-sectional view of the scroll compressor connected to the refrigerant circuit. It is a figure which shows Embodiment 4, and is a figure which shows the refrigerant circuit provided with the scroll compressor.

Explanation of symbols

  1 fixed scroll, 1a fixed scroll base plate, 1b plate-like spiral tooth, 1c Oldham ring guide groove, 1f discharge port, 1h injection port, 2 swing scroll, 2a swing scroll base plate, 2b plate spiral tooth, 2c swing Dynamic bearing, 2d thrust surface, 2e Oldham ring guide groove, 2f boss, 2h orbiting scroll back pressure chamber, 2i base plate outer peripheral space, 2j bleed hole, 2k bleed hole opening, 3 compliant frame, 3a thrust bearing, 3c main bearing, 3h auxiliary bearing, 3l intermediate pressure adjustment valve, 3m intermediate pressure adjustment spring, 3p pressure adjustment valve storage space, 3s communication path, 3t intermediate pressure adjustment spring presser, 4 main shaft, 4b swing shaft, 4c main shaft 4d countershaft part, 4e spindle balancer, 4g spindle through hole, 6 subframe, 6a countershaft , 8 Motor rotor, 9 Oldham ring, 9a Oscillating claw, 9c Fixed claw, 10 Sealed container, 10a Suction pipe, 10b Discharge pipe, 10c Injection pipe, 10e Refrigerating machine oil, 10f injector, 10h Injection pipe holder, 10j Shock absorber, 15 guide frame, 15a upper fitting cylindrical surface, 15b lower fitting cylindrical surface, 15f frame space, 15g outer peripheral surface, 15m intermediate pressure adjustment spring, 15p pressure adjustment valve storage space, 15t intermediate pressure adjustment spring presser, 16a Upper seal material, 16b Lower seal material, 32 Intermediate pressure adjustment valve, 51 Flow control valve, 52 Injection refrigerant supply pipe, 53 Condenser, 54 Depressurizer, 55 Evaporator, 60 Injection plate, 60a Injection path, 60b Injection ® emission path, 70 compression chamber, 80 injection connection pipe, 80a injection connection pipe bend.

Claims (5)

A compression mechanism portion having a compliant frame in which a plate-like spiral teeth of a fixed scroll and a swing scroll are meshed to form a compression chamber and a main bearing for supporting a main shaft for driving the swing scroll is formed in a sealed container. In the scroll compressor provided in
An injection path provided on the back surface of the base plate of the fixed scroll and connected from the sealed container;
An injection port communicating with the compression chamber through the fixed scroll base plate from the injection path;
A bleed hole provided in the base plate of the rocking scroll, for guiding the refrigerant gas pressurized in the compression chamber;
Provided in a thrust bearing portion of the compliant frame, comprising: the bleed hole; and a communication passage disposed so as to allow communication only in a limited section per one rotation of the main shaft, A frame space that is pressure-blocked from the inside of the sealed container is formed on a side surface, and a section in which the compression chamber and the frame space communicate with each other is always in a section in which the injection port communicates with the compression chamber. A scroll compressor characterized by that.   The injection port provided in the fixed scroll is disposed so as to communicate with the outermost compression chamber after the outermost compression chamber formed by the plate-like spiral teeth is formed. The scroll compressor according to claim 1.   2. The scroll compressor according to claim 1, wherein the injection path communicating from the sealed container to the compression chamber has a portion having a diameter smaller than an inner diameter of the apparatus-side pipe connected to the outside of the compressor.   The tip of the injection pipe that joins the injection path provided in the front fixed scroll and the refrigeration cycle is formed of a highly rigid member, the inner diameter of the tip of the injection pipe is made smaller than the other injection paths, and the tip of the injection pipe is 2. The scroll compressor according to claim 1, wherein the injection path is formed by press-fitting into the injection path provided in the fixed scroll.   The injection pipe connecting the injection path and the refrigeration cycle is taken out from the side surface of the sealed container, and the injection pipe connected to the injection pipe is partially bent until it is connected to the injection refrigerant supply pipe in the refrigeration cycle. The scroll compressor according to claim 1, further comprising a curved portion of the injection connecting pipe.

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