JP4980412B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor.

  Conventionally, each plate-like spiral tooth provided in an airtight container for the purpose of improving the instability that the compliant frame and the orbiting scroll easily relieve due to flapping of the orbiting scroll caused by a slight disturbance. A fixed scroll and an oscillating scroll meshed so as to form a compression chamber therebetween, and a main shaft for supporting the oscillating scroll in the axial direction and driving the oscillating scroll. A compliant frame supporting in the axial direction and a guide frame supporting the compliant frame in the radial direction and fixed to the sealed container, the axial direction of the compliant frame relative to the guide frame In a scroll compressor in which the oscillating scroll can be moved in the axial direction by moving the frame, between the compliant frame and the guide frame Frame - to form a beam space frame - through the beam space higher than the suction pressure, sucrose and characterized in that a pressure below the discharge pressure or less - Le compressor has been proposed (e.g., see Patent Document 1).

JP 2000-161254 A

  In a vertical scroll compressor in which the inside of the sealed container is high pressure (discharge pressure) and the compression mechanism is placed on the motor, the sump for storing the refrigerating machine oil at the bottom of the sealed container has high pressure (discharge pressure). ing. In order to supply this high-pressure refrigerating machine oil to the compression mechanism section located in the upper part of the hermetic container, a pressure lower than the high pressure (discharge pressure) near the compression mechanism section side of the spindle, for example, an intermediate pressure space (boss section Space, which will be explained later). Due to the differential pressure between the high-pressure oil sump and the intermediate-pressure boss space, the high-pressure refrigerating machine oil rises inside the main shaft and is supplied to the intermediate-pressure boss space. This oiling method is called a differential pressure oiling method.

  For example, if there is a wiring mistake when installing a unit (for example, an air conditioner) (wiring mistake to the terminal of the unit (so-called reverse phase that shifts the phase order of the three-phase power supply)) Is activated and no power is supplied to the scroll compressor.

  However, when the reverse phase prevention relay is activated due to a wiring mistake when the unit is installed and the scroll compressor does not start, the reverse phase prevention relay may be short-circuited or removed to forcibly start the scroll compressor.

  When the scroll compressor is started in a so-called reverse phase in which the phase order of the three-phase power source is shifted, a reverse operation opposite to the normal rotation is performed.

  When the differential pressure oil supply type scroll compressor is continuously operated in the reverse direction, the compression mechanism portion does not compress the refrigerant but expands the refrigerant.

  In the case of the operation in which the compression mechanism section expands the refrigerant, the pressure does not increase in the sealed container, so that no differential pressure is generated between the oil sump and the boss space. Therefore, there is a problem that the main shaft is seized due to poor lubrication of the bearing of the compression mechanism.

  The present invention has been made to solve the above-described problems, and can prevent seizure of the shaft due to poor lubrication of the bearing portion during reverse rotation operation, improve reliability, and improve quality. A scroll compressor that can be realized is provided.

A scroll compressor according to the present invention includes a compression mechanism section, an electric motor that drives the compression mechanism section, and refrigeration oil that lubricates the compression mechanism section in a sealed container, and the inside of the sealed container is a high-pressure scroll compressor. There,
The compression mechanism is
A fixed scroll in which plate-like spiral teeth are formed on one surface of the base plate portion and the base plate portion;
A plate-like spiral having the same shape as that of the fixed scroll plate-like spiral teeth is provided on one surface of the base plate portion and the fixed plate portion, and is combined with the plate-like spiral teeth of the fixed scroll to form a compression chamber. With dynamic scrolling,
Oldham ring to prevent the rotation of the orbiting scroll,
A main shaft that is fixed to the electric motor and drives the orbiting scroll;
A guide frame fixed to the hermetic container, supporting the main shaft in the radial direction and coupled to the fixed scroll;
The base plate of the orbiting scroll is such that the pressure in the boss space of the orbiting scroll is lower than the pressure in the sealed container during reversal operation of the electric motor, and the refrigerating machine oil is supplied to the compression mechanism by the differential pressure. Are provided with communication holes for communicating the boss space and the compression chamber in the expansion stroke.

  In the scroll compressor according to the present invention, during the reverse rotation operation of the electric motor, the pressure in the back pressure space of the orbiting scroll is lower than the pressure in the sealed container, and the compressor oil is supplied to the compression mechanism by the differential pressure. In addition, the base plate of the orbiting scroll is provided with a communication hole that communicates the boss space of the orbiting scroll and the compression chamber during the expansion stroke, preventing shaft seizure due to poor lubrication of the bearing during reverse rotation operation. In addition, the reliability can be improved and the quality can be improved.

FIG. 3 is a diagram illustrating the first embodiment, and is a longitudinal sectional view of the scroll compressor 100. FIG. 3 is a diagram showing the first embodiment, and is a longitudinal sectional view in the vicinity of a fixed scroll 1. FIG. 5 shows the first embodiment, and shows a valve passage 17d that communicates with the plate-like spiral tooth 1b of the fixed scroll 1 from the direction perpendicular to the suction pressure space 1g. FIG. 5 shows the first embodiment, and is a cross-sectional view of an intake check valve assembly 17. FIG. 3 shows the first embodiment, and is an enlarged view near the portion A in FIG. 2. FIG. 3 is a diagram illustrating the first embodiment and is a diagram illustrating an Oldham ring 9 ((a) is a plan view, (b) is a right side view, and (c) is a front view). FIG. 5 shows the first embodiment, and is a plan view of the fixed scroll 1 on the plate-like spiral tooth 1b side. FIG. 3 is a diagram illustrating the first embodiment, and is a vertical cross-sectional view of an orbiting scroll 2. FIG. 5 shows the first embodiment, and is a plan view of the surface on the opposite side of the plate-like spiral teeth 2b of the orbiting scroll 2; FIG. 5 shows the first embodiment, and is a plan view of the surface of the orbiting scroll 2 on the plate-like spiral tooth 2b side. FIG. 3 shows the first embodiment, and is a longitudinal sectional view of a compliant frame 3. FIG. 3 shows the first embodiment, and is a longitudinal sectional view of a main shaft 4. FIG. 5 shows the first embodiment, and is a longitudinal sectional view of the guide frame 15. FIG. 3 shows the first embodiment, and is a longitudinal sectional view of the electric motor 20. FIG. 3 is a diagram illustrating the first embodiment, and is a longitudinal sectional view of a subframe 6. FIG. 3 is a diagram illustrating the first embodiment and is a diagram illustrating a trajectory of a communication hole 2k that accompanies rocking of the rocking scroll 2; In the diagram showing the first embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k is as follows. The figure which showed about °. In the diagram showing the first embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k is as follows. The figure which showed about °. In the diagram showing the first embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the rocking scroll 2 with respect to the fixed scroll 1 and the communication hole 2k is as follows. The figure which showed about °. In the diagram showing the first embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k is the rotation angle 540 ° of the main shaft 4 and the rotation angle 630. The figure which showed about °. FIG. 5 shows the first embodiment, and shows the relationship between the pressure in the first chamber 20a and the rotation angle of the main shaft 4. Fig. 5 shows the first embodiment, and shows a connection of a three-phase induction motor. Fig. 5 shows the first embodiment, and shows a connection of a single-phase induction motor. The figure which shows Embodiment 1 and is a figure which shows an example of the refrigerant circuit of the air conditioner 200 in which the scroll compressor 100 is integrated. FIG. 5 shows the first embodiment, and is a ph diagram (Mollier diagram) of the refrigeration cycle of the air conditioner 200. FIG. FIG. 5 shows the second embodiment, and is a partial longitudinal sectional view of a scroll compressor 300. FIG. 5 shows the second embodiment and is a longitudinal sectional view of the orbiting scroll 2 showing the communication hole 2n. FIG. 6 is a view showing the second embodiment, and is a longitudinal sectional view of the orbiting scroll 2 showing a communication hole 2n and a communication check valve 2p. FIG. 5 shows the second embodiment, and is an enlarged view of the communication check valve 2p. In the diagram showing the second embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2n is as follows. The figure which showed about °. In the diagram showing the second embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2n is the rotation angle 180 ° of the main shaft 4 and the rotation angle 270. The figure which showed about °. In the diagram showing the second embodiment, assuming that the suction completion state is a rotation angle of 0 °, the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2n is the rotation angle 360 ° of the main shaft 4 and the rotation angle 450. The figure which showed about °. FIG. 6 shows the second embodiment, and shows the relationship between the pressure in the first chamber 20a and the rotation angle of the main shaft 4.

Embodiment 1 FIG.
First, this embodiment is characterized in the following points.
(1) Since the discharge space pressure Pd does not become larger than the suction space pressure Ps during the reverse rotation operation in a general scroll compressor, no differential pressure is generated between the upper end surface and the lower end surface of the main shaft, and therefore the differential pressure cannot be supplied to the bearing portion. The main shaft will burn. However, the scroll compressor of the present embodiment has a pressure lower than the discharge space pressure to the boss space of the orbiting scroll including the upper end of the main shaft so that each bearing portion can be oiled by the discharge differential pressure oil supply method during reverse operation. In order to draw in (the pressure in the spiral of the expansion stroke), a communication hole to the boss space is provided in the base plate portion of the orbiting scroll. By doing so, a differential pressure is generated between the upper end surface and the lower end surface of the main shaft during the reverse rotation operation, and it is possible to supply the differential pressure and supply oil to each bearing portion, thereby preventing shaft seizure and improving reliability. I can do it.
(2) In the scroll compressor of the present embodiment, a pressure lower than the discharge space pressure (in the expansion stroke) to the boss space of the oscillating scroll including the oscillating bearing so that differential pressure oil can be supplied to the bearing during reverse rotation. The position of the communication hole to the boss space in the orbiting scroll for drawing the pressure in the swirl is that the refrigerating machine oil is continuously sucked up from the oil sump at the bottom of the hermetic container during reverse rotation operation, so that the refrigerating machine oil is not depleted. 360 ° position where the boss space is not always in communication with the communication hole, and where the refrigerant in the scroll is not compressed into the boss space during forward rotation (the pressure during compression in the compression chamber is greater than the boss space pressure) Provide at a smaller position. By doing so, oil depletion during reverse operation can be prevented and reliability can be improved. Further, it is possible to prevent the compressed gas from flowing out into the boss space during the forward rotation operation, and to prevent the performance from being deteriorated during the forward rotation operation.
(3) The scroll compressor according to the present embodiment has a relief valve and a valve presser at a position corresponding to the suction pressure space on the surface opposite to the plate-like spiral tooth of the base plate portion of the fixed scroll. A relief valve assembly is provided. When a scroll compressor provided with a suction check valve assembly is in a state where a liquid refrigerant is filled in a compression chamber, if a reverse rotation operation opposite to normal rotation is started for some reason, a pumping pressure due to liquid compression is generated. Due to the pumping pressure, the plate-like spiral teeth of the fixed scroll are displaced, so that the mechanism is locked or the compression performance is lowered. In the relief valve assembly, when liquid compression occurs in the compression chamber, the liquid refrigerant is released to the outside of the compression chamber (inner space of the hermetic container) to suppress the generation of pumping pressure due to liquid compression.

  1 to 25 show the first embodiment. FIG. 1 is a longitudinal sectional view of the scroll compressor 100, FIG. 2 is a longitudinal sectional view of the fixed scroll 1, and FIG. 3 is a plate-like spiral tooth of the fixed scroll 1. FIG. 4 is a diagram showing a valve passage 17d communicating with the suction pressure space 1g from a direction perpendicular to 1b, FIG. 4 is a sectional view of the suction check valve assembly 17, FIG. 9 (a) is a plan view, (b) is a right side view, (c) is a front view), FIG. 7 is a plan view of the fixed scroll 1 on the plate-like spiral tooth 1b side, and FIG. FIG. 9 is a plan view of the surface on the opposite side of the plate-like spiral tooth 2b of the orbiting scroll 2, FIG. 10 is a plan view of the surface of the orbiting scroll 2 on the plate-like spiral tooth 2b side, and FIG. 11 is a longitudinal sectional view of the compliant frame 3, FIG. 12 is a longitudinal sectional view of the main shaft 4, and FIG. FIG. 14 is a longitudinal sectional view of the electric motor 20, FIG. 15 is a longitudinal sectional view of the subframe 6, FIG. 16 is a diagram showing a trajectory of the communication hole 2k accompanying the swing of the swing scroll 2, and FIG. FIG. 18 shows the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k with respect to the rotation angle 0 ° and the rotation angle 90 °. FIG. 19 shows the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k, with the rotation angle 180 ° and the rotation angle 270 ° of the main shaft 4, assuming the completed state as the rotation angle 0 °. The correlation between the relative position of the oscillating scroll 2 with respect to the fixed scroll 1 and the communication hole 2k is shown for the rotation angle 360 ° and the rotation angle 450 ° of the main shaft 4 with the suction completion state being 0 °. FIG. 20 shows the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k with the suction completion state being the rotation angle 0 °, with respect to the rotation angle 540 °, the rotation angle, and 630 ° of the main shaft 4. FIG. 21 is a view showing the relationship between the pressure in the first chamber 20a and the rotation angle of the main shaft 4, FIG. 22 is a view showing the connection of the three-phase induction motor, and FIG. 23 is the connection of the single-phase induction motor. FIG. 24 is a diagram illustrating an example of a refrigerant circuit of an air conditioner 200 in which the scroll compressor 100 is incorporated, and FIG. 25 is a ph diagram (Mollier diagram) of a refrigeration cycle of the air conditioner 200.

  As shown in FIG. 1, the scroll compressor 100 includes at least a compression mechanism unit 40, an electric motor 20, a main shaft 4 that connects the compression mechanism unit 40 and the electric motor 20, and a compression mechanism of the main shaft 4. And a refrigerating machine oil 10e stored in a sump 10g at the bottom of the hermetic container 10 and an end portion on the opposite side of the portion 40 (the sub-shaft portion 4d (see FIG. 12)).

  In the compression mechanism 40, at least each plate-like spiral tooth 1b (see FIGS. 2 and 7) and plate-like spiral tooth 2b (see FIGS. 8 and 10) form a compression chamber 1d (see FIG. 2) between them. The fixed scroll 1 and the orbiting scroll 2 that are engaged with each other, the Oldham ring 9, the compliant frame 3, and the guide frame 15 are provided.

  Hereinafter, main components of the compression mechanism unit 40 will be described in order.

  The fixed scroll 1 will be described with reference mainly to FIGS. 2 to 7 (the Oldham ring 9 is also referred to). The fixed scroll 1 is fastened to the guide frame 15 by bolts (not shown) in the vicinity of the outer peripheral portion thereof.

  As shown in FIG. 7, a plurality of holes are formed in the vicinity of the outer peripheral portion of the base plate 1a of the fixed scroll 1 (12 in FIG. 7). Two positioning holes 1j that determine the position of the fixed scroll 1 with respect to the guide frame 15 are positioned substantially diagonally.

  The holes other than the two positioning holes 1j are bolt holes 1k when the fixed scroll 1 is fastened to the guide frame 15 with bolts. In FIG. 7, ten bolt holes 1k are provided. This is an example, and the number of bolt holes 1k may be arbitrary.

  A plate-like spiral tooth 1b is formed on one surface (lower side in FIG. 2) of the base plate portion 1a.

  As shown in FIG. 7, a pair of Oldham guide grooves 1 c are formed on the outer periphery of the fixed scroll 1 on a straight line deviated from the center line of the fixed scroll 1 by a predetermined dimension d1.

  A pair of fixed scroll side claws 9c (see FIG. 6) of the Oldham ring 9 is engaged with the Oldham guide groove 1c so as to be slidable back and forth.

  As shown in FIG. 6, the Oldham ring 9 has a pair of fixed scroll side claws 9c having a phase of about 180 ° on the same surface, and a phase difference of about 90 ° from the pair of fixed scroll side claws 9c. A pair of orbiting scroll side claws 9a having the following phase is formed.

  The pair of orbiting scroll side claws 9 a is engaged with the orbiting scroll Oldham guide groove 2 e (see FIG. 9) of the orbiting scroll 2. The Oldham ring 9 prevents the swing scroll 2 from rotating.

  Further, a valve passage 17d is provided to communicate with the suction pressure space 1g from a direction perpendicular to the plate-like spiral tooth 1b of the fixed scroll 1 (see FIG. 3).

  A suction pipe 10a (FIGS. 1 and 2) is press-fitted into the fixed scroll 1 through the hermetic container 10 so as to communicate with the plate-like spiral tooth 1b of the fixed scroll 1 from the direction perpendicular to the suction pressure space 1g. .

  A suction check valve assembly 17 (see FIG. 4) is provided so as to slide in the valve passage 17d (see FIG. 3).

  As shown in FIG. 4, the suction check valve assembly 17 includes a suction check valve 17a and a spring 17b. The suction check valve 17a is biased by a spring 17b so as to close in the direction of the suction pipe 10a. The suction check valve 17a stops in contact with the end face of the suction pipe 10a and is sealed to prevent the refrigerant from flowing backward.

  A discharge port 1f through which high-pressure refrigerant gas is discharged is formed at a substantially central portion of the base plate portion 1a of the fixed scroll 1 (see FIGS. 2 and 7).

  In FIG. 7, two elongated holes 1m formed in the vicinity of the relief hole 1h are omitted in detail, but they also serve as suction ports for sucking refrigerant into the compression chamber 1d.

  The plate-like spiral teeth 1b (see FIG. 2) of the fixed scroll 1 and the plate-like spiral teeth 2b (see FIG. 3) of the orbiting scroll 2 are engaged with each other to form a compression chamber 1d (see FIG. 2). The

  A relief valve assembly 50 is provided at a position corresponding to the suction pressure space 1g on the surface of the base plate portion 1a of the fixed scroll 1 opposite to the plate-like spiral teeth 1b.

  As shown in FIG. 5, the relief valve assembly 50 includes a relief valve 50a and a valve presser 50b.

  A relief hole 1 h passes through the base plate portion 1 a of the fixed scroll 1. The relief hole 1h communicates with the suction pressure space 1g. A relief valve 50a closes the opening of the relief hole 1h opposite to the suction pressure space 1g so that it can be opened and closed.

  As will be described in detail later, when the scroll compressor 100 is in a state where the compression chamber 1d is filled with the liquid refrigerant, a pumping pressure due to liquid compression is generated when the reverse rotation operation opposite to the normal rotation is started for some reason. Due to the pumping pressure, the plate-like spiral tooth 1b of the fixed scroll 1 is displaced, so that the mechanism is locked or the compression performance is lowered. When liquid compression occurs in the compression chamber 1d, the relief valve assembly 50 allows the liquid refrigerant to escape to the outside of the compression chamber 1d (internal space of the hermetic container 10) and suppress the generation of pumping pressure due to liquid compression.

  The orbiting scroll 2 will be described with reference to FIGS. The orbiting scroll 2 is provided with a plate-like spiral tooth 2b having substantially the same shape as the plate-like spiral tooth 1b of the fixed scroll 1 on one surface of the base plate portion 2a. The compression chamber 1d (see FIG. 2) is formed in combination with 1b.

  As shown in FIG. 8, a hollow cylindrical boss portion 2f is formed at a substantially central portion of the surface of the base plate portion 2a opposite to the plate-like spiral teeth 2b, and the swing shaft portion 4b at the upper end of the main shaft 4 is formed. And are rotatably engaged.

  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 surface of the base plate portion 2a opposite to the plate-like spiral teeth 2b.

  As shown in FIG. 9, a pair of Oldham guide grooves 2e having a phase difference of 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed on the outer periphery of the base plate 2a in a substantially straight line. Yes. A rocking scroll side claw 9a (see FIG. 6) of the Oldham ring 9 is engaged with the Oldham guide groove 2e so as to be freely slidable.

  The base plate 2a is provided with an extraction hole 2j that allows the compression chamber 1d and the thrust surface 2d to communicate with each other, and has a structure that extracts refrigerant gas that is being compressed and guides it to the thrust surface 2d.

  Further, the base plate 2a is provided with a communication hole 2k that allows the compression chamber 1d and the boss space 2h to communicate with each other (see FIGS. 8 and 10). The communication hole 2k that allows the compression chamber 1d and the boss portion space 2h to communicate with each other is the most important component in the present embodiment.

  Although details will be described later, during reverse operation of the scroll compressor 100, the boss space 2h of the orbiting scroll 2 is set to a lower pressure than the oil sump 10g (inside the sealed container 10), and the refrigerating machine oil 10e is transferred from the sump 10g to the main shaft 4 In order to lead to the boss part space 2h via the hollow space 4g, the communication hole 2k is provided.

  The compliant frame 3 will be described with reference to FIG. The compliant frame 3 includes two upper and lower upper cylindrical surfaces 3d and a lower cylindrical surface 3e provided on the outer peripheral portion thereof, and an upper cylindrical surface 15a and a lower cylindrical surface 15b (see FIG. 5) provided on the inner peripheral portion of the guide frame 15. 13)) in the radial direction.

  In a substantially central part of the compliant frame 3, a main bearing 3c and a sub main part which are separated from the compliant frame 3 and support the main shaft 4 which is rotationally driven by the electric motor 20 (see FIGS. 1 and 14) in the radial direction. A bearing 3h is fitted.

  Further, a communication passage 3s penetrating in the axial direction from the surface of the thrust bearing 3a is provided, and the opening 3k on the thrust bearing side is arranged to face the swing scroll extraction hole 2j.

  The main shaft 4 will be described with reference to FIG. At the upper end portion of the main shaft 4, there is formed a rocking shaft portion 4b that is rotatably engaged with the rocking bearing 2c of the rocking scroll 2 and is eccentric from the main shaft portion 4c by a predetermined dimension.

  A main shaft balancer 4e is shrink fitted on the lower side of the swinging shaft portion 4b.

  Also, a main shaft portion 4c that is rotatably engaged with the main bearing 3c and the sub main bearing 3h of the compliant frame 3 is formed under a portion where the main shaft balancer 4e is fitted.

  In addition, a lower shaft portion 4c is formed with a lower shaft portion 4d that is rotatably engaged with the auxiliary bearing 6a (see FIG. 15) of the subframe 6. The rotor 8 of the electric motor 20 is shrink-fitted between the auxiliary shaft portion 4d and the main shaft portion 4c (see FIG. 1).

  An upper balancer 8a is fixed to an end ring 8c (see FIG. 14) at the upper end of the rotor 8. Further, the lower balancer 8b is fixed to the end ring 8c (see FIG. 14) at the lower end of the rotor 8 at a phase of 180 ° with the upper balancer 8a.

  A total of three balancers (main shaft balancer 4e (see FIG. 12), upper balancer 8a, and lower balancer 8b) balance the static and dynamic of the main shaft 4.

  Further, an oil pipe 4f is press-fitted into the lower end of the main shaft 4 so that the refrigerating machine oil 10e accumulated in the oil sump 10g at the bottom of the sealed container 10 is sucked up.

  The guide frame 15 will be described with reference to FIG. In FIG. 13, a part of the compliant frame 3 and the sealed container 10 are shown by a one-dot chain line.

  The outer peripheral surface 15g of the guide frame 15 is fixed to the sealed container 10 by shrink fitting or welding. A discharge pipe provided between the compression mechanism 40 and the electric motor 20 for discharging the high-pressure refrigerant gas discharged from the discharge port 1f of the fixed scroll 1 by the cutout portion 15c formed by cutting out the outer peripheral portion of the guide frame 15. A flow path 10h (see FIG. 13) leading to 10b (see FIG. 1) is secured. The notch 15c is provided at a position opposite to the discharge pipe 10b (a position where the phase is approximately 180 ° different).

  Further, on the inner peripheral surface of the guide frame 15, an upper cylindrical surface 3d formed on the outer peripheral surface of the compliant frame 3, an upper cylindrical surface 15a that engages with the lower cylindrical surface 3e, a lower cylindrical surface 15b, and a seal Two sealing grooves for storing the material are provided.

  A seal material 16a is installed in the seal groove 15h, and a seal material 16b is installed in the seal groove 15i. A frame space 15f (see FIG. 13) formed by the inner peripheral surface of the guide frame 15 and the outer peripheral surface of the compliant frame 3 sealed by using these two sealing materials 16a and 16b is a communication path of the compliant frame 3. It communicates only with 3s, and has a structure that encloses refrigerant gas in the middle of compression supplied from the extraction hole 2j.

  The electric motor 20 will be described with reference to FIG. The electric motor includes at least a stator 7 and a rotor 8. Here, the electric motor 20 is an induction motor (single phase, three phase). However, other brushless DC motors may be used.

  The stator 7 includes at least a stator core (not shown), a winding, and an insulating material (slot cell or the like).

  The stator core has a substantially donut-like overall cross-sectional shape, and a core back having a ring-like cross-sectional shape is formed on the outer peripheral side. From the core back, teeth are radially provided on the inner side at substantially equal intervals in the circumferential direction.

  The circumferential width of the tooth portion is substantially uniform in the radial direction. That is, the tooth portion has a substantially parallel shape toward the inner peripheral side of the rotor core. The tip part on the inner diameter side of the tooth part has an arc shape in which both sides spread in the circumferential direction.

  A space surrounded by two adjacent tooth portions and a part of the core back is called a slot. The number of teeth and the number of slots are the same.

  Since the circumferential width of the tooth portion is substantially uniform in the radial direction, the circumferential width of the slot gradually increases from the inside toward the outside.

  The inner peripheral side (rotor side) of the slot is open. The opening portion on the inner peripheral side (rotor side) of this slot is called a slot opening portion.

  The winding is inserted into the slot through this slot opening.

  Each slot is provided with a winding wound in a three-phase or single-phase concentrated winding method or distributed winding method via an insulating material (not shown) such as a slot cell. For the winding, a magnet wire or the like in which an insulating film is applied to the outside of the copper wire is used.

  The stator core is a thin electromagnetic steel sheet (for example, a non-oriented electrical steel sheet with a thickness of about 0.1 to 1.0 mm (the crystal axis direction of each crystal is set so as not to be biased toward a specific direction of the steel sheet and exhibit magnetic properties) The material is randomly arranged as much as possible))) in a predetermined shape with a die, and a predetermined number (multiple) is laminated.

  In the rotor 8 arranged on the inner diameter side of the stator 7 via a gap (not shown), a squirrel-cage winding is formed by die casting on a rotor core in which electromagnetic steel plates are laminated.

  Similarly to the stator core, the rotor core is also formed by punching a thin electromagnetic steel sheet (for example, a non-oriented electrical steel sheet having a thickness of about 0.1 to 1.0 mm) into a predetermined shape with a die, and a predetermined number of sheets (multiple Sheet) is constructed by stacking.

  The gap between the stator 7 and the rotor 8 has a radial dimension of about 0.2 to 2.0 mm, for example.

  Although not shown, the stator 7 is formed with a hole or notch through which the refrigerating machine oil 10e falling from the upper part to the lower part in the hermetic container 10 passes.

  The subframe 6 will be described with reference to FIG. The subframe 6 supports the end portion (subshaft portion 4d (see FIG. 12)) of the main shaft 4 on the opposite side of the compression mechanism portion 40.

  The sub frame 6 is formed with a sub bearing 6a on which the sub shaft portion 4d of the main shaft 4 slides rotatably.

  Further, the sub-frame 6 is formed with an oil hole 6b for dropping the refrigerating machine oil 10e falling downward from the electric motor 20 into the sump 10g.

  Next, the basic operation of the scroll compressor 100 using the compliant frame 3 of the high pressure shell type (the inside of the sealed container 10 is the high pressure side of the refrigeration cycle) will be described.

  By the operation of the scroll compressor 100, the suction refrigerant (low-pressure refrigerant) is sucked from the suction pipe 10a from the suction side of the refrigeration cycle. Due to the suction pressure of the suction refrigerant, the suction check valve 17 a overcomes the spring force and is pushed down to the valve stop surface (not shown), and the suction refrigerant is formed by the plate-like spiral teeth 2 b of the fixed scroll 1 and the swing scroll 2. Enters the compression chamber 1d.

  The orbiting scroll 2 driven by the electric motor 20 via the main shaft 4 performs an eccentric orbiting motion to reduce the volume of the compression chamber 1d. Due to this compression stroke, the suction refrigerant becomes high pressure and is discharged into the sealed container 10 from the discharge port 1 f of the fixed scroll 1.

  In the compression stroke, the intermediate-pressure refrigerant gas in the middle of compression is guided to the frame space 15f from the extraction hole 2j (see FIG. 8) of the orbiting scroll 2 through the communication passage 3s of the compliant frame 3, and this space. An intermediate pressure atmosphere is maintained (see FIG. 2 except for the extraction holes 2j). The high-pressure discharge gas fills the sealed container 10 with a high-pressure atmosphere, and is discharged from the discharge pipe 10b to the outside of the scroll compressor 100.

  The refrigerating machine oil 10e stored in the oil sump 10g at the bottom of the sealed container 10 penetrates the main shaft 4 in the axial direction due to a differential pressure (a differential pressure between the high pressure in the sealed container 10 and the intermediate pressure in the boss space 2h). It passes through the hollow space 4g and is guided to the rocking bearing space 2g (see FIG. 8). The refrigerating machine oil 10e having an intermediate pressure due to the squeezing action of the rocking bearing space 2g fills a boss space 2h that is a space surrounded by the rocking scroll 2 and the compliant frame 3.

  It is guided to the low pressure space (suction pressure space 1g) via the pressure regulating valve 18 (see FIGS. 1 and 2) that connects the boss space 2h and the low pressure atmosphere space, and is sucked into the compression chamber 1d together with the low pressure refrigerant gas. The The refrigerating machine oil 10e is discharged into the sealed container 10 from the discharge port 1f together with the high-pressure refrigerant gas by the compression stroke.

  In the scroll compressor 100 according to the present embodiment, the boss portion space 2h has a plate-like spiral tooth 1b of the fixed scroll 1 and a plate-like spiral tooth 2b of the orbiting scroll 2 within a predetermined range of the rotation angle of the main shaft 4. Is characterized in that it communicates with the outermost peripheral chamber (this chamber is defined as the outermost peripheral chamber) formed by meshing the two via the communication hole 2k.

  The operational effects of the above features in the scroll compressor 100 of the present embodiment will be described later.

  A compression chamber 1 d (outermost peripheral chamber) formed by meshing the plate-like spiral teeth 1 b of the fixed scroll 1 and the plate-like spiral teeth 2 b of the orbiting scroll 2 is gradually compressed by the rotation of the main shaft 4. , Move to the center while increasing pressure.

  For example, refer to FIG. It is assumed that when the rotation angle of the main shaft 4 is 0 °, the refrigerant suction is completed, and a sealed first chamber 20a (outermost peripheral chamber) is formed. As the rotation of the main shaft 4 proceeds, the sealed first chamber 20a moves to the center (near the discharge port 1f) while increasing the pressure while reducing the volume.

  The compression chamber 1d shown in FIG. 2 has an outermost periphery (a rotation angle of the main shaft 4 in FIG. 17 is approximately 0 ° to about 4 °) engaged with the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2. 90 °) substantially coincides with the first chamber 20a.

  The outermost peripheral chamber formed on the outermost periphery of the meshing of the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the swing scroll 2 is newly formed every 360 ° of the rotation angle of the main shaft 4. .

  The compression chamber 1d shown in FIG. 2 has an outermost periphery for meshing between the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2 that are newly formed every rotation angle 360 ° of the main shaft 4. The outermost peripheral chamber formed in FIG.

  Here, one of the outermost peripheral chambers formed on the outermost periphery of the meshing of the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2 formed one after another is One chamber 20a (compression chamber 1d) is used.

  FIG. 16 shows the locus of rotation of the communicating hole 2k formed in the base plate portion 2a of the orbiting scroll 2 accompanying the oscillation of the orbiting scroll 2, but it does not communicate with the boss space 2h in the figure. The communication hole 2k is indicated by a thin solid line circle, and the communication hole 2k communicating with the boss space 2h is indicated by a thick solid line circle.

  As shown in FIG. 16, the communication hole 2 k communicates with the boss space 2 h within a range of approximately 90 ° of the rotation angle of the main shaft 4. In the other range of approximately 270 ° of the rotation angle of the main shaft 4, the communication hole 2 k is closed by the surface of the thrust bearing 3 a of the compliant frame 3.

  Here, the rotation angle of the main shaft 4 is defined. As shown in FIG. 17, the rotation angle of the main shaft 4 is set to 0 ° when the first chamber 20a completes the suction of the refrigerant.

  The “rotation angle 0 ° of the main shaft 4” in FIG. 16 coincides with (rotation angle 0 ° of the main shaft 4) in FIG. Further, “the rotation angle 90 ° of the main shaft 4” in FIG. 16 coincides with (the rotation angle 90 ° of the main shaft 4) in FIG.

Accordingly, the opening on the compliant frame 3 side of the communication hole 2k must satisfy the following conditions.
(1) The opening on the compliant frame 3 side of the communication hole 2k communicates with the boss space 2h between the rotation angles 0 ° to 90 ° (schematic range) of the main shaft 4.
(2) The opening on the compliant frame 3 side of the communication hole 2k does not communicate with the boss space 2h between the rotation angles 90 ° to 360 ° (schematic range) of the main shaft 4 (the communication hole 2k It is closed by the surface of the thrust bearing 3a of the client frame 3).

  The communication with the first chamber 20a (one of the compression chambers 1d) of the opening (plate spiral tooth 2b side) opposite to the compliant frame 3 of the communication hole 2k is at least the compliant frame 3 of the communication hole 2k. When the opening on the side communicates with the boss space 2h, it is essential to be in a communicating state.

  When the opening on the compliant frame 3 side of the communication hole 2k is not in communication with the boss space 2h, the first opening of the communication hole 2k on the side opposite to the compliant frame 3 (plate spiral tooth 2b side) The communication with the chamber 20a (one of the compression chambers 1d) may or may not be communicated.

  17 to 20 show the correlation between the relative position of the orbiting scroll 2 with respect to the fixed scroll 1 and the communication hole 2k with the suction completion state as the rotation angle of 0 °, and the rotation angles of the main shaft 4 of 0 °, 90 °, and 180 °. It shows about 270 °, 360 °, 450 °, 540 °, and 630 °.

  As shown in FIG. 17, when the rotation angle of the main shaft 4 is 0 °, the suction is completed and the first chamber 20a is formed. At this time, the volume of the first chamber 20a is the largest. As shown in the figure, the first chamber 20a communicates with the communication hole 2k.

  Moreover, as shown in FIG. 16, since the communication hole 2k has started communication with the boss part space 2h, the boss part space 2h and the first chamber 20a are in communication.

  When the main shaft 4 is rotated from 0 ° to 90 °, the first chamber 20a moves counterclockwise and inward while reducing its volume. Even if the rotation angle of the main shaft 4 is 90 °, it communicates with the communication hole 2k.

  Further, as shown in FIG. 16, since the communication hole 2k is still in communication with the boss part space 2h, the boss part space 2h and the first chamber 20a are in communication.

  As shown in FIG. 18, when the main shaft 4 rotates from 90 ° to 90 ° to 180 °, the first chamber 20a moves counterclockwise and inward while further reducing its volume. When the rotation angle of the main shaft 4 is 180 °, it does not communicate with the communication hole 2k. Somewhere the main shaft 4 rotates between 90 ° and 180 °, the opening on the plate-like spiral tooth 2b side of the communication hole 2k is not in communication with the first chamber 20a. The plate-like spiral tooth 1b of the fixed scroll 1 closes the opening of the communication hole 2k on the plate-like spiral tooth 2b side. Alternatively, the opening on the plate-like spiral tooth 2b side of the communication hole 2k opens to the space of the next outermost peripheral chamber candidate that has not yet been sucked.

  As shown in FIG. 18, when the main shaft 4 is rotated from 180 ° to 90 ° to 270 °, the first chamber 20a moves counterclockwise and inward while further reducing its volume. When the rotation angle of the main shaft 4 is 270 °, the communication hole 2k opens to the space of the next outermost peripheral chamber candidate that has not yet been sucked, so the opening of the communication hole 2k on the plate-like spiral tooth 2b side is The first chamber 20a is not in communication.

  As shown in FIG. 19, when the main shaft 4 is rotated from 270 ° to 90 ° to 360 ° (the main shaft 4 is rotated once), the first chamber 20a is turned inward in the counterclockwise direction. Move while reducing its volume. When the rotation angle of the main shaft 4 is 360 °, the communication hole 2k is opened in the space of the outermost peripheral chamber next to the suction, so that the opening on the plate-like spiral tooth 2b side of the communication hole 2k The chamber 20a is not in communication.

  As shown in FIG. 19, when the main shaft 4 is rotated from 360 ° to 90 ° to 450 °, the first chamber 20a moves counterclockwise and inward while further reducing its volume. When the rotation angle of the main shaft 4 is 450 °, the communication hole 2k is opened in the space of the outermost peripheral chamber next to the suction, so that the opening of the communication hole 2k on the plate-like spiral tooth 2b side is the first The chamber 20a is not in communication.

  As shown in FIG. 20, when the main shaft 4 is rotated from 450 ° to 90 ° to 540 °, the first chamber 20a moves in the counterclockwise direction and inward while further reducing its volume. The first chamber 20a communicates with the discharge port 1f when the main shaft 4 has a rotation angle of 540 °. Therefore, the pressure in the first chamber 20a is substantially equal to the discharge pressure Pd. Precisely, the main chamber 4 is in front of the rotation angle 540 °, and the first chamber 20a communicates with the discharge port 1f.

  As shown in FIG. 20, when the main shaft 4 is rotated from 540 ° to 90 ° to 630 °, the first chamber 20a is counterclockwise and inward, while further reducing its volume, the discharge port 1f. Move in communication with the.

  FIG. 21 is a graph showing the relationship between the pressure in the first chamber 20a and the rotation angle of the main shaft 4. From the rotation angle 0 ° of the main shaft 4 in which the suction of the sucked refrigerant is completed and the first chamber 20a is formed. The change of the pressure of the 1st chamber 20a to the rotation angle 630 degrees of the main axis | shaft 4 is shown.

  When the rotation angle of the main shaft 4 is 0 °, the suction of the suction refrigerant is completed and the first chamber 20a is formed, so the pressure in the first chamber 20a is equal to the suction pressure Ps.

  Thereafter, as the main shaft 4 rotates, the first chamber 20a moves inward while reducing its volume, and the pressure in the first chamber 20a gradually increases.

  As described above, the boss portion space 2h and the first chamber 20a communicate with each other in the section where the rotation angle of the main shaft 4 is 0 ° to 90 °. As shown also in FIG. 21, in the section where the rotation angle of the main shaft 4 is 0 ° to 90 °, the pressure in the first chamber 20a is lower than the intermediate pressure in the boss space 2h. Accordingly, the refrigerant in the boss space 2h and the refrigerating machine oil 10e are drawn into the first chamber 20a. Therefore, even if the boss part space 2h communicates with the first chamber 20a, the pressure of the first chamber 20a does not escape to the boss part space 2h.

  When the rotation angle of the main shaft 4 exceeds 90 °, the boss portion space 2h and the first chamber 20a are not in communication with each other, and the pressure in the first chamber 20a continues to rise. In the specifications of the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2 in FIGS. 17 to 20, the rotation angle of the main shaft 4 is somewhere between 450 ° and 540 °, The chamber 20a communicates with the discharge port 1f, and the pressure in the first chamber 20a becomes the discharge pressure Pd.

  The effect by which the boss | hub part space 2h and the 1st chamber 20a are connecting in the area of the rotation angle 0 degrees-90 degrees of the main axis | shaft 4 is demonstrated.

  When a three-phase or single-phase induction motor is used as the electric motor 20, in assembling a unit (for example, an air conditioner), the glass terminal 10f (see FIG. 1) of the scroll compressor 100 in the three-phase induction motor is used. The motor 20 may be reversed in the production line test due to a connection error of the power supply terminal, an operation capacitor connection error in the single-phase induction motor, or the like.

  In the case of a bushyless DC motor driven by an inverter, a protective circuit for detecting the reverse phase of the power supply and shutting off the energization of the bushyless DC motor is incorporated in the normal drive circuit, so that the glass terminal 10f of the scroll compressor 100 ( If there is a connection error of the power terminal to (see FIG. 1), the scroll compressor 100 will not start. However, if the drive circuit detects the reverse phase of the power supply and there is a connection error to the brushless DC motor, the scroll compressor may reverse.

  In the connection of the three-phase induction motor of FIG. 22, if the three power terminals (U phase, V phase, W phase) are correctly connected to the glass terminal 10f (see FIG. 1) of the scroll compressor 100, the motor 20 is predetermined. Perform forward rotation. However, for example, as shown in FIG. 22, if the connection between the U phase and the V phase is wrong (the V phase of the power supply is connected to the U phase winding and the U phase of the power supply is connected to the V phase winding), The electric motor 20 performs a reverse rotation operation opposite to a predetermined normal rotation operation.

  In the connection of the single-phase induction motor shown in FIG. 23, the operating capacitor is normally connected in series with the auxiliary winding, and the series circuit is connected in parallel with the main winding.

  If the operating capacitor is connected to the main winding and the series circuit is connected in parallel to the auxiliary winding (in parentheses in FIG. 23) due to a connection error of the operating capacitor, the motor 20 is opposite to the predetermined forward rotation operation. Perform reverse operation.

  Here, an example of the refrigerant circuit of the unit (air conditioner 200) in which the scroll compressor 100 is incorporated will be described with reference to FIG.

  The air conditioner 200 includes an outdoor unit 201 and an indoor unit 202. The outdoor unit 201 and the indoor unit 202 are connected by a gas pipe 205 and a liquid pipe 207 which are connection pipes (extension pipes).

  The outdoor unit 201 includes a gas side valve 214 for connecting the gas pipe 205 and a liquid side valve 215 for connecting the liquid pipe 207.

  The indoor unit 202 includes a gas side connection part 216 for connecting the gas pipe 205 and a liquid side connection part 217 for connecting the liquid pipe 207.

  For the gas pipe 205 and the liquid pipe 207, copper pipes having a predetermined diameter and length are used. When the air conditioner 200 is installed, the gas pipe 205 and the liquid pipe 207 are made according to the local situation.

  The gas pipe 205 and the liquid pipe 207 are fixed by flare nuts (not shown) provided in the gas side valve 214, the liquid side valve 215, the gas side connection part 216, and the liquid side connection part 217, respectively.

  The outdoor unit 201 includes a compressor that compresses the refrigerant (here, the scroll compressor 100), a four-way valve 204 that switches between the cooling operation and the heating operation (cooling operation in the off state), and a heat source side heat exchanger. An outdoor heat exchanger 211, a first pressure reducing device 210, an intermediate pressure receiver 209, and a second pressure reducing device 208.

  In FIG. 24, the four-way valve 204 that switches the refrigerant flow direction between the cooling operation and the heating operation is indicated by a solid line in the refrigerant flow during the cooling / heating operation. Moreover, the flow path of the refrigerant | coolant at the time of heating operation is shown with the broken line.

  The outdoor heat exchanger 211 that is a heat source side heat exchanger operates as a condenser during the cooling operation, and operates as an evaporator during the heating operation. In addition, the outdoor fan (not shown) blows air to the outdoor heat exchanger 211 to promote heat exchange between the refrigerant and the air.

  For example, an electronic expansion valve is used for the first decompressor 210 and the second decompressor 208.

  In the intermediate pressure receiver 209, the gas-liquid two-phase refrigerant flows in, exchanges heat with the suction pipe 218 of the scroll compressor 100, and flows out as liquid refrigerant.

  The indoor unit 202 includes an indoor heat exchanger 206 that is a use side heat exchanger. The indoor heat exchanger 206 operates as an evaporator during the cooling operation. Moreover, it operates as a condenser during heating operation. In addition, air is sent to the indoor heat exchanger 206 by an indoor blower (not shown) to promote heat exchange between the refrigerant and the air, and conditioned air is sent to the conditioned space. Let the refrigerant circuit of the indoor unit 202 be an indoor refrigerant circuit.

  The operation of the refrigerant circuit of the air conditioner 200 will be described with reference to FIG. 25 for each of the heating operation and the cooling operation.

  During the heating operation, the high-pressure and high-temperature gas refrigerant (point 1 in FIG. 25) discharged from the scroll compressor 100 passes through the four-way valve 204, passes through the gas-side valve 214, the gas pipe 205, and the gas-side connection portion 216 to the room. It flows into the heat exchanger 206.

  In the indoor heat exchanger 206, the gas refrigerant is cooled and condensed by exchanging heat with room air (lower than the temperature of the gas refrigerant). In the vicinity of the outlet of the indoor heat exchanger 206, it becomes a high-pressure liquid refrigerant (point 2 in FIG. 25). The high-pressure liquid refrigerant is supercooled at a predetermined temperature lower than the condensation temperature.

  The high-pressure liquid refrigerant that has exited the indoor heat exchanger 206 flows into the second decompression device 208 via the liquid-side connection portion 217, the liquid pipe 207, and the liquid-side valve 215. In the second decompression device 208, the high-pressure liquid refrigerant is decompressed to become a medium-pressure gas-liquid two-phase refrigerant (point 3 in FIG. 25).

  The medium-pressure gas-liquid two-phase refrigerant that has exited the second decompression device 208 flows into the intermediate-pressure receiver 209. The medium-pressure gas-liquid two-phase refrigerant flowing into the medium-pressure receiver 209 exchanges heat with the low-pressure and low-temperature gas refrigerant flowing through the suction pipe 218 of the scroll compressor 100 to become a medium-pressure liquid refrigerant (see FIG. 25). Point 4).

  The medium-pressure liquid refrigerant exiting the intermediate-pressure receiver 209 is decompressed by the first decompression device 210 and becomes a low-pressure gas-liquid two-phase refrigerant (point 5 in FIG. 25).

  The low-pressure gas-liquid two-phase refrigerant that has exited the first decompression device 210 flows into the outdoor heat exchanger 211. In the outdoor heat exchanger 211, the low-pressure gas-liquid two-phase refrigerant evaporates by exchanging heat with the outside air (temperature is higher than that of the low-pressure gas-liquid two-phase refrigerant). And it becomes a low-pressure gas refrigerant (point 6 of Drawing 25).

  Further, the low-pressure gas refrigerant is heated by exchanging heat with the medium-pressure gas-liquid two-phase refrigerant of the medium-pressure receiver 209 (point 7 in FIG. 25), and is sucked into the scroll compressor 100.

  During the cooling operation, the high-pressure and high-temperature gas refrigerant (point 1 in FIG. 25) discharged from the scroll compressor 100 flows into the outdoor heat exchanger 211.

  In the outdoor heat exchanger 211, the gas refrigerant is cooled and condensed by exchanging heat with the outside air (lower than the temperature of the gas refrigerant). In the vicinity of the outlet of the outdoor heat exchanger 211, it becomes a high-pressure liquid refrigerant (point 2 in FIG. 25). The high-pressure liquid refrigerant is supercooled at a predetermined temperature lower than the condensation temperature.

  The high-pressure liquid refrigerant that has exited the outdoor heat exchanger 211 flows into the first decompression device 210. In the first pressure reducing device 210, the high-pressure liquid refrigerant is depressurized to become a medium-pressure gas-liquid two-phase refrigerant (point 3 in FIG. 25).

  The medium-pressure gas-liquid two-phase refrigerant that has exited the first decompression device 210 flows into the intermediate-pressure receiver 209. The medium-pressure gas-liquid two-phase refrigerant flowing into the medium-pressure receiver 209 exchanges heat with the low-pressure and low-temperature gas refrigerant flowing through the suction pipe 218 of the scroll compressor 100 to become a medium-pressure liquid refrigerant (see FIG. 25). Point 4).

  The medium-pressure liquid refrigerant exiting the medium-pressure receiver 209 is decompressed by the second decompression device 208 and becomes a low-pressure gas-liquid two-phase refrigerant (point 5 in FIG. 25).

  The low-pressure gas-liquid two-phase refrigerant exiting the second decompression device 208 flows into the indoor heat exchanger 206 through the liquid side valve 215, the liquid pipe 207, and the liquid side connection portion 217. In the indoor heat exchanger 206, the low-pressure gas-liquid two-phase refrigerant evaporates by exchanging heat with room air (temperature is higher than that of the low-pressure gas-liquid two-phase refrigerant). And it becomes a low-pressure gas refrigerant (point 6 of Drawing 25).

  Further, the low-pressure gas refrigerant is heated by exchanging heat with the medium-pressure gas-liquid two-phase refrigerant of the medium-pressure receiver 209 (point 7 in FIG. 25), and is sucked into the scroll compressor 100.

  In the case of using a three-phase or single-phase induction motor for the electric motor 20, when assembling a unit (for example, an air conditioner), the glass terminal 10f (see FIG. 1) of the scroll compressor 100 in the three-phase induction motor is used. Reference will be made to problems in the case where the motor 20 is reversed in the production line test due to a connection error of the power supply terminal, a connection error of the operating capacitor in the single-phase induction motor, or the like.

  In the production line, in the air conditioner 200, the outdoor unit 201 and the indoor unit 202 are assembled separately.

  When the refrigerant circuit is assembled using the scroll compressor 100 or the like, the outdoor unit 201 is a charge port in which refrigerant (for example, R22, R410A, R407C, etc.) is provided between the four-way valve 204 and the outdoor heat exchanger 211. To the refrigerant circuit. At this time, the four-way valve 204 is turned off to form a cooling operation circuit. Therefore, the discharge side of the scroll compressor 100 and the outdoor heat exchanger 211 are in communication. The refrigerant filled in the refrigerant circuit from the charge port is filled into the outdoor heat exchanger 211 and the sealed container 10 of the scroll compressor 100.

  In the production line of the air conditioner 200, the outdoor unit 201 being manufactured is connected to the dummy indoor unit 202, and a shipping test is performed. At this time, if there is a connection error of the power supply terminal to the glass terminal 10f (see FIG. 1) of the scroll compressor 100 in the three-phase induction motor, or an operation capacitor connection error in the single-phase induction motor, the scroll compressor 100 At start-up, the electric motor 20 operates in reverse.

By the reverse rotation operation of the electric motor 20, the compression mechanism 40 becomes an expander instead of a compressor. That is, the operation at the start of the scroll compressor 100 having no discharge valve after charging the refrigerant is as follows. The scroll compressor 100 is provided with a suction check valve assembly 17. Reference is also made to a scroll compressor that does not include a suction check valve assembly 17.
(1) One compression chamber 1d (referred to as compression chamber A) communicating with the discharge port 1f sucks the refrigerant in the hermetic container 10 (the refrigerant in the entire refrigeration cycle is balanced at the same pressure), When the reverse rotation of the main shaft 4 proceeds and the compression chamber A is closed, the main shaft 4 moves outward while expanding its volume. At this time, the pressure in the compression chamber A gradually decreases.
(2) When the compression chamber A communicates with the boss space 2h via the communication hole 2k, the pressure in the compression chamber A is lower than the balance pressure of the refrigeration cycle. The pressure drops. The volume ratio between the boss portion space 2h and the compression chamber A is, for example, about 10: 1, and the boss portion after the compression chamber A communicates with the boss portion space 2h by the respective pressures before communicating with the volume ratio. The pressure in the space 2h and the compression chamber A is determined. When the reverse rotation of the main shaft 4 further proceeds, the pressure in the boss portion space 2h and the compression chamber A further decreases as the volume of the compression chamber A increases.
(3) When the reverse rotation of the main shaft 4 further proceeds and the compression chamber A is released, the compression chamber A communicates with the suction pressure space 1g. Since the suction pressure space 1g is closed by the suction check valve assembly 17, the amount of refrigerant in the suction pressure space 1g increases.
(4) The next compression chamber B formed inside the compression chamber A performs the same operation. Therefore, the pressure in the boss space 2h further decreases. Further, the amount of refrigerant in the suction pressure space 1g further increases.
(5) By repeating the above operation, the pressure in the boss space 2h becomes lower than the pressure in the sealed container 10 (substantially equal to the balance pressure of the refrigeration cycle before starting). That is, since the pressure of the oil sump 10g becomes larger than the pressure of the boss part space 2h, the refrigerating machine oil 10e ascends the hollow space 4g of the main shaft 4 and flows into the boss part space 2h. Thereby, oil can be supplied to each bearing such as the rocking bearing 2c. Therefore, seizure of the main shaft 4 during the reverse rotation operation of the electric motor 20 that occurs when there is no communication hole 2k that allows the boss portion space 2h and the compression chamber 1d to communicate with each other can be suppressed.
(6) Although the amount of refrigerant in the suction pressure space 1g continues to increase, when the pressure in the suction pressure space 1g exceeds a predetermined pressure, the relief valve 50a opens and the refrigerant in the suction pressure space 1g is released into the sealed container 10. .

Therefore, in the scroll compressor 100 provided with the suction check valve assembly 17, the following components are essential in order to suppress seizure of the main shaft 4 during the reverse rotation operation of the electric motor 20.
(1) The rotation angle of the main shaft 4 in which the outermost peripheral chamber is formed by the engagement of the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2 is 0 °. A communication hole 2k that allows the boss portion space 2h and the outermost peripheral chamber to communicate with each other when the rotation angle is approximately 0 ° to 90 ° (a predetermined rotation angle range of the main shaft 4).
(2) The relief hole 1h of the base plate portion 1a of the fixed scroll 1 can be freely opened and closed at a position corresponding to the suction pressure space 1g on the surface opposite to the plate-like spiral tooth 1b of the base plate portion 1a of the fixed scroll 1. A relief valve assembly 50 including a relief valve 50a and a valve presser 50b that are closed.

  In the scroll compressor that does not include the suction check valve assembly 17, the refrigerant flowing into the suction pressure space 1 g flows out to the suction side of the refrigeration cycle when starting the reverse rotation operation, so that the relief valve assembly 50 is unnecessary. . The scroll compressor that does not include the suction check valve assembly 17 is (1) a main shaft in which the outermost peripheral chamber is formed by meshing the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2. For example, when the rotation angle of the main shaft 4 is approximately 0 ° to 90 ° (a predetermined rotation angle range of the main shaft 4), the communication hole that communicates the boss space 2h with the outermost peripheral chamber. 2k is an essential component.

  Next, reference will be made to the reverse operation due to a connection mistake at the time of installation of the air conditioner 200 including the outdoor unit 201 on which the scroll compressor 100 is mounted and the indoor unit 202.

  In this case, the scroll compressor 100 using a three-phase induction motor as the electric motor 20 is a target. When the electric motor 20 is a brushless DC motor driven by an inverter, the outdoor unit 201 at the time of installation is installed when the drive circuit does not include a protection circuit that detects the reverse phase of the power supply and cuts off the power to the brushless DC motor. In the connection of the three-phase power supply to the power supply connection terminal, if the total order is shifted, the scroll compressor 100 is reversed, which is a target. In the case of the scroll compressor 100 using a single-phase induction motor for the electric motor 20, even if the phase (two-phase) order is shifted in the connection of the single-phase power supply to the power supply connection terminal of the outdoor unit 201 at the time of installation, the electric motor No 20 reverse operation occurs. At the time of service (replacement) of the operating capacitor after installation, the occurrence of reverse operation due to a connection mistake with a very low probability is considered.

  The air conditioner 200 having the indoor unit 202 and the outdoor unit 201 needs to connect the indoor unit 202 and the outdoor unit 201 locally by connecting piping at the time of installation.

  The indoor unit 202 includes a gas side connection part 216 for connecting the gas pipe 205 and a liquid side connection part 217 for connecting the liquid pipe 207.

  At the time of factory shipment, nitrogen gas or the like is sealed in the refrigerant circuit (indoor heat exchanger 206) of the indoor unit 202. The two open ends of the refrigerant circuit of the indoor unit 202 are closed with a flare nut with a cap, for example, so that nitrogen gas does not leak to the outside (gas side connection part 216, liquid side connection part 217). .

  The refrigerant circuit of the outdoor unit 201 is filled with a predetermined amount of refrigerant at the time of factory shipment. The scroll compressor 100 is filled with a predetermined amount of refrigerating machine oil 10e for lubricating the compression mechanism.

  Valves (a gas side valve 214 for connecting the gas pipe 205 and a liquid side valve 215 for connecting the liquid pipe 207) are connected to the two open ends of the refrigerant circuit of the outdoor unit 201, respectively. It is designed not to leak. Flares nuts with caps similar to the indoor unit 202 are attached to the valves of the outdoor unit 201 (the gas side valve 214 for connecting the gas pipe 205 and the liquid side valve 215 for connecting the liquid pipe 207). Yes. Since the refrigerant circuit is closed by the valve, the flare nut with the cap is necessary for connecting the connection pipe at the time of installation. The reason for using a flare nut with a cap similar to that of the indoor unit 202 is to share parts.

  A method for connecting the indoor unit 202 and the outdoor unit 201 when the air conditioner 200 is installed will be described.

  First, a flare nut with a cap that closes two open ends in the refrigerant circuit of the indoor unit 202 is removed using a tool. At this time, the nitrogen gas sealed in the refrigerant circuit of the indoor unit 202 is released to the atmosphere.

  Moreover, the flare nut with a cap attached to the valves of the outdoor unit 201 (the gas side valve 214 for connecting the gas pipe 205 and the liquid side valve 215 for connecting the liquid pipe 207) is also removed using a tool. . At this time, since the valve is closed, the refrigerant is kept in the refrigerant circuit of the outdoor unit 201.

  Next, the caps are removed from the flare nuts with caps of the indoor unit 202 and the outdoor unit 201 (four in total).

  Furthermore, the copper pipe (two pieces) used as the connection pipe is cut into a predetermined length. The predetermined length substantially coincides with the distance between the installed indoor unit 202 and the outdoor unit 201.

  Insert two flare nuts with caps removed into the two connecting pipes. And the both ends of each of two connection piping are expanded.

  Four flare nuts are fastened to the original parts of the indoor unit 202 and the outdoor unit 201. This completes the connection of the connection pipe.

  Air or air containing nitrogen gas remaining without being released remains in the refrigerant circuit and the connection pipe of the indoor unit 202 that has been connected.

  Therefore, a vacuum pump is connected to the refrigerant charge port provided in the valve of the outdoor unit 201 (which pushes the closing valve open and communicates with the connection pipe side), and the inside of the refrigerant circuit of the indoor unit 202 and the connection pipe is evacuated. I do.

  When evacuation of the refrigerant circuit of the indoor unit 202 and the inside of the connection pipe is completed, the two valves of the outdoor unit 201 (the gas side valve 214 for connecting the gas pipe 205 and the liquid side valve for connecting the liquid pipe 207). 215) is opened, the refrigerant filled in the outdoor unit 201 is moved to the whole refrigerant circuit, and the installation work is completed.

  A copper pipe having a predetermined diameter and length is used for the connection pipe (gas pipe 205 and liquid 207). When the air conditioner 200 is installed, the gas pipe 205 and the liquid pipe 207 are made according to the local situation.

  In one example, additional charging of the refrigerant is unnecessary until the connection pipe (gas pipe 205 and liquid 207) is up to 30 m.

  When the connection pipe (gas pipe 205 and liquid 207) is 30 m or longer, a predetermined additional refrigerant is filled according to the connection pipe size and pipe length. The procedure is to connect the two valves of the outdoor unit 201 (the gas side valve 214 for connecting the gas pipe 205 and the liquid pipe 207 after the evacuation of the refrigerant circuit of the indoor unit 202 and the inside of the connecting pipe is completed. The liquid side valve 215) is opened to open the refrigerant indoors, and while performing a test operation (cooling operation), the refrigerant charge port (close valve) provided on the valve of the outdoor unit 201 is opened to the connection piping side. The additional refrigerant is charged (to be precise, drawn into the refrigerant circuit).

  At this time, the refrigerant is charged from the refrigerant charge port of the gas side valve 214 to the low pressure side of the refrigeration cycle.

  Assume that the phase order is shifted and the phases are reversed in connection of the three-phase power source to the power source connection terminal of the outdoor unit 201 at the time of installation. When a trial operation (cooling operation) in which additional refrigerant is charged in this state is performed, the scroll compressor 100 performs a reverse operation.

  The reverse rotation operation of the scroll compressor 100 at this time is substantially the same as that in the shipping test in the production line of the air conditioner 200.

  If the liquid refrigerant is present in the scroll compressor 100 using the suction check valve assembly 17 and the engine is started and operated in the reverse direction, the pressure in the suction pressure space 1g may rise rapidly and the compression mechanism 40 may be destroyed. is there.

  When the air conditioner 200 is installed, it is very unlikely that the scroll compressor 100 starts in a state in which liquid refrigerant is present and that it is reversely operated.

  As a condition for such a state, when the evacuation of the refrigerant circuit of the indoor unit 202 and the connection pipe is completed, the two valves of the outdoor unit 201 (the gas side for connecting the gas pipe 205 are connected). The valve 214 and the liquid side valve 215 for connecting the liquid pipe 207 are opened, and when the refrigerant filled in the outdoor unit 201 is moved to the entire refrigerant circuit, the operation is interrupted, and additional refrigerant is charged. The work is carried over to the next day.

  In particular, in a cold region, when the temperature of the scroll compressor 100 decreases due to cold air at night, the refrigerant sleeps in the scroll compressor 100 (liquid refrigerant is stored in the scroll compressor 100).

  In this state, for example, in order to charge additional refrigerant, a test operation is started, and when there is a connection mistake and the scroll compressor 100 using the suction check valve assembly 17 starts reverse rotation, the pressure in the suction pressure space 1g is increased. There is a possibility that the compression mechanism 40 may be suddenly broken and destroyed.

  However, the scroll compressor 100 according to the present embodiment uses the relief valve assembly 50 including the relief valve 50a and the valve presser 50b when the suction check valve assembly 17 is used. The assembly 50 can avoid a sudden rise in the pressure in the suction pressure space 1g.

  In the normal rotation operation of the scroll compressor 100, the communication hole 2k that allows the compression chamber 1d and the boss space 2h to communicate with each other is in a state where the suction of the refrigerant has been completed, and the sealed outermost peripheral chamber (first chamber 20a When the rotation angle of the main shaft 4 is 0 °, the communication hole 2k communicates the outermost peripheral chamber and the boss space 2h in a section where the rotation angle of the main shaft 4 is approximately 0 ° to 90 °. As shown in FIG. 21, in this section (the rotation angle of the main shaft 4 is approximately 0 ° to 90 °), the pressure (intermediate pressure) in the boss space 2h is higher than the pressure in the outermost peripheral chamber. The refrigerant does not escape to the boss space 2h and does not affect the performance of the scroll compressor 100.

  In the case of reverse rotation operation of the scroll compressor 100, if the compression chamber 1d and the boss space 2h are communicated with each other through the communication hole 2k in the entire range of the rotation angle of the main shaft 4, the refrigeration of the oil sump rising to the boss space 2h is performed. There is a possibility that the machine oil 10e increases and the refrigerating machine oil 10e is lost in the oil sump. If the rotation angle of the main shaft 4 when the suction of the refrigerant is completed and the sealed outermost peripheral chamber (first chamber 20a) is formed is 0 °, the rotation angle of the main shaft 4 is approximately 0 ° to 90 °. Since the communication hole 2k communicates the outermost peripheral chamber and the boss part space 2h in the section of °, there is a risk that the amount of the refrigerating machine oil 10e that rises in the boss part space 2h increases, and the refrigerating machine oil 10e disappears in the sump. There are few.

As described above, the scroll compressor 100 according to the present embodiment has the following effects.
(1) In a general scroll compressor, since the discharge space pressure Pd does not become larger than the suction space pressure Ps during the reverse rotation operation, no differential pressure is generated between the upper end surface and the lower end surface of the main shaft 4, so that the bearing portion can be supplied with a differential pressure. The main shaft 4 is burned out. However, the scroll compressor 100 of the present embodiment discharges the discharge space pressure to the boss space of the orbiting scroll 2 including the upper end portion of the main shaft 4 so that each bearing portion can be oiled by the discharge differential pressure oil supply method during the reverse rotation operation. A communication hole 2k to the boss space (boss space 2h) is provided in the base plate portion 2a of the orbiting scroll 2 in order to draw a pressure Pm '(pressure in the spiral of the expansion stroke) lower than Pd. By doing so, a differential pressure is generated between the upper end surface and the lower end surface of the main shaft 4 during the reverse rotation operation, so that the differential pressure can be supplied and oil can be supplied to each bearing portion, preventing shaft seizure and improving reliability. I can plan.
(2) In the scroll compressor 100 of the present embodiment, a pressure lower than the discharge space pressure Pd to the boss space 2h of the orbiting scroll 2 including the orbiting bearing 2c so that the bearing portion can be supplied with differential pressure during reverse rotation operation. The position of the communicating hole 2k to the boss space 2h in the orbiting scroll 2 for drawing Pm '(pressure in the spiral of the expansion stroke) is such that the refrigerating machine oil 10e continues from the oil sump 10g at the bottom of the hermetic container 10 during reverse rotation operation. In order to prevent exhaustion of the refrigerating machine oil 10e, the 360 ° boss part space 2h and the communication hole 2k do not communicate with each other, and the refrigerant in the middle of compression in the scroll does not flow into the boss part space 2h during forward rotation operation. It is provided at a position (a position where the pressure during compression of the compression chamber becomes smaller than the boss space pressure). By doing so, oil depletion during reverse operation can be prevented and reliability can be improved. Further, it is possible to prevent the compressed gas from flowing out into the boss space 2h during the forward operation, and to prevent the performance from being deteriorated during the forward operation.
(3) The scroll compressor 100 of the present embodiment includes a relief valve 50a at a position corresponding to the suction pressure space 1g on the surface opposite to the plate-like spiral teeth 1b of the base plate portion 1a of the fixed scroll 1. A relief valve assembly 50 including a valve presser 50b is provided. When the scroll compressor 100 including the suction check valve assembly 17 is in a state in which the compression chamber 1d is filled with liquid refrigerant, for some reason, the pumping pressure due to liquid compression is generated when the reverse rotation operation opposite to the normal rotation is started. . Due to the pumping pressure, the plate-like spiral tooth 1b of the fixed scroll 1 is displaced, so that the mechanism is locked or the compression performance is lowered. When liquid compression occurs in the compression chamber 1d, the relief valve assembly 50 allows the liquid refrigerant to escape to the outside of the compression chamber 1d (internal space of the hermetic container 10) and suppress the generation of pumping pressure due to liquid compression.

Embodiment 2. FIG.
In a general scroll compressor, since the discharge space pressure Pd does not become larger than the suction space pressure Ps during the reverse rotation operation, no differential pressure is generated between the upper end surface and the lower end surface of the main shaft 4, so the differential pressure cannot be supplied to the bearing portion. 4 will burn out.

  In the scroll compressor 300 of the second embodiment, the pressure Pm ′ (expansion stroke) is lower than the discharge space pressure Pd in the spiral to the upper end space of the main shaft 4 so that each bearing portion can be supplied with a discharge differential pressure oil supply method during reverse operation. Is provided with a communication hole 2n to the boss space 2h so that refrigerant does not flow from the communication hole 2n into the spiral during forward rotation. 2p is provided. By doing so, a differential pressure is generated between the upper end surface and the lower end surface of the main shaft 4 during the reverse rotation operation, so that the differential pressure can be supplied and oil can be supplied to each bearing portion, preventing shaft seizure and improving reliability. I can plan. Further, it is possible to prevent the compressed gas from flowing out into the boss space during the forward rotation operation, and to prevent the performance from being deteriorated during the forward rotation operation.

  In the scroll compressor 300, a pressure Pm ′ (in the spiral of the expansion stroke) lower than the discharge space pressure Pd is applied to the boss space 2h of the orbiting scroll 2 including the orbiting bearing 2c so that differential pressure oil can be supplied to the bearing during reverse rotation. The refrigerating machine oil 10e is continuously sucked up from the oil sump 10g at the bottom of the hermetic container 10 during the reverse rotation operation, so that the refrigerating machine oil 10e is located at the position of the communication hole 2n to the upper end of the main shaft 4 in the orbiting scroll. Is provided at a position where the 360 ° boss portion space 2h and the communication hole 2n do not communicate with each other (a position where the pressure during compression of the compression chamber becomes smaller than the boss portion space pressure). By doing so, oil depletion during reverse operation can be prevented and reliability can be improved.

  26 to 32 are diagrams showing the second embodiment, FIG. 26 is a partial longitudinal sectional view of the scroll compressor 300, FIG. 27 is a longitudinal sectional view of the orbiting scroll 2 showing the communication hole 2n, and FIG. 28 is a communication hole. FIG. 29 is an enlarged view of the communication check valve 2p, and FIG. 30 shows the swing scroll with respect to the fixed scroll 1 with the rotation completion angle set to 0 °. FIG. 31 shows the correlation between the relative position of 2 and the communication hole 2n with respect to the rotation angle 0 ° and the rotation angle 90 ° of the main shaft 4. FIG. FIG. 32 is a diagram showing the correlation between the relative position of the scroll 2 and the communication hole 2n with respect to the rotation angle 180 ° and the rotation angle 270 ° of the main shaft 4. FIG. Movement FIG. 33 is a diagram showing the correlation between the relative position of the crawl 2 and the communication hole 2n with respect to the rotation angle 360 ° and the rotation angle 450 ° of the main shaft 4. FIG. 33 shows the relationship between the pressure in the first chamber 20a and the rotation angle of the main shaft 4. It is a figure which shows a relationship.

The scroll compressor 300 of the second embodiment shown in FIG. 26 is different from the scroll compressor 100 of the first embodiment in the following points. Since other configurations are the same, description thereof will be omitted. The following components are provided in part B of FIG.
(1) A communication hole 2n that connects the inside of the spiral (compression chamber 1d) of meshing between the plate-like spiral tooth 1b of the fixed scroll 1 and the plate-like spiral tooth 2b of the orbiting scroll 2, and the boss space 2h; A check valve storage portion 2q that communicates with the communication hole 2n and opens to the spiral (compression chamber 1d) is provided.
(2) The communication check valve 2p is provided so that the refrigerant does not flow into the boss space 2h from the inside of the spiral through the communication hole 2n during the forward rotation operation.

  The scroll compressor 300 is not provided with a communication hole 2k that allows the compression chamber 1d (first chamber 20a, outermost peripheral chamber) provided in the base plate portion 2a to communicate with the boss space 2h.

  As shown in FIG. 27, the base plate portion 2a of the orbiting scroll 2 has a communication hole 2n communicating with the boss space 2h, and a space between the plate-like spiral teeth 2b communicating with the communication hole 2n. And a check valve storage portion 2q for storing the communication check valve 2p.

  As shown in FIG. 28, the communication check valve 2p is stored in the check valve storage portion 2q. The communication check valve 2p closes the opening on the check valve storage portion 2q side of the communication hole 2n communicating with the boss space 2h.

  As shown in FIG. 29, the communication check valve 2p includes a check valve portion 2p-1 and a spring 2p-2 that urges the check valve portion 2p-1 toward the communication hole 2n.

  The communication check valve 2p opens when the difference between the pressure in the boss space 2h and the pressure in the spiral (compression chamber 1d) becomes larger than the force of the spring 2p-2, and the boss space 2h and the spiral (compression chamber 1d) Communicate.

  During the forward rotation operation of the scroll compressor 300, since the pressure in the boss space 2h is larger than the pressure in the spiral (compression chamber 1d), the communication check valve 2p is kept closed.

  As shown in FIGS. 30 to 32, the check valve storage portion 2 q communicates with the first chamber 20 a at a predetermined angle exceeding the rotation angle 0 ° of the main shaft 4 and exceeds the rotation angle 270 ° of the main shaft 4. It communicates to a predetermined angle.

  During the reverse rotation operation of the scroll compressor 300, the main shaft 4 communicates with the first chamber 20a at a predetermined angle exceeding the rotation angle 0 °, and the expansion is performed at a predetermined angle exceeding the rotation angle 270 ° of the main shaft 4. Since the stroke causes the pressure in the first chamber 20a to be lower than the pressure in the boss portion space 2h, the check valve portion 2p-1 opens and the boss portion space opens when the force due to the differential pressure exceeds the force of the spring 2p-2. 2h communicates with the first chamber 20a. As a result, the pressure in the boss space 2h decreases. By repeating this, the pressure in the boss space 2h becomes lower than the pressure in the sump 10g (pressure in the sealed container 10), and differential pressure oil supply to the boss space 2h is possible.

The communication hole 2k of the first embodiment, the inside of the spiral (compression chamber 1d) meshing with the plate-like spiral tooth 1b of the fixed scroll 1 of the second embodiment and the plate-like spiral tooth 2b of the orbiting scroll 2, and the boss A communication hole 2n that communicates with the partial space 2h, and a check valve storage portion 2q that communicates with the communication hole 2n and opens in the spiral (compression chamber 1d) are provided. When compared with the configuration in which the communication check valve 2p is provided so that the refrigerant does not flow into the boss space 2h, the following points are different.
(1) The communication hole 2k according to the first embodiment is such that the refrigerant flows from the compression chamber 1d into the boss space 2h when the pressure in the compression chamber 1d exceeds a predetermined value during forward rotation. There is a limit to the angle (rotation angle of the main shaft 4) with which the space 2h communicates. On the other hand, in the method using the communication check valve 2p according to the second embodiment, even if the pressure in the compression chamber 1d is increased during the forward rotation operation, the refrigerant flows into the boss space 2h because the pressure is blocked by the communication check valve 2p. do not do. Therefore, the degree of freedom of the communication angle is increased as compared with the first embodiment.
(2) The communication hole 2k according to the first embodiment needs to be closed by the thrust bearing 3a of the compliant frame 3, but the communication check valve 2p according to the second embodiment does not need this.

  In the first and second embodiments, the scroll compressors 100 and 300 using the compliant frame 3 have been described. However, the present invention can also be applied to a scroll compressor that does not use the compliant frame 3.

  1 fixed scroll, 1a base plate portion, 1b plate-like spiral tooth, 1c Oldham guide groove, 1d compression chamber, 1f discharge port, 1g suction pressure space, 1h relief hole, 1k bolt hole, 1j positioning hole, 2 swing scroll 2a Base plate part, 2b Plate-like spiral tooth, 2c Oscillating bearing, 2d Thrust surface, 2e Oldham guide groove, 2f Boss part, 2g Oscillating bearing space, 2h Boss part space, 2j Extraction hole, 2k Communication hole, 2n Communication hole, 2p communication check valve, 2p-1 check valve part, 2p-2 spring, 2q check valve storage part, 3 compliant frame, 3a thrust bearing, 3c main bearing, 3d upper cylindrical surface, 3e lower side Cylindrical surface, 3h Sub main bearing, 3k opening, 3s communication passage, 4 main shaft, 4b swing shaft portion, 4c main shaft portion, 4d sub shaft portion, 4e main shaft balancer, 4f oil pie 4g hollow space, 6 subframe, 6a sub bearing, 6b oil hole, 7 stator, 8 rotor, 8a upper balancer, 8b lower balancer, 8c end ring, 9 Oldham ring, 9a swing scroll side claw, 9c fixed Scroll side claw, 10 Airtight container, 10a Suction pipe, 10b Discharge pipe, 10e Refrigerating machine oil, 10f Glass terminal, 10g Oil reservoir, 10h Flow path, 15 Guide frame, 15a Upper cylindrical surface, 15b Lower cylindrical surface, 15c Notch Part, 15f frame space, 15g outer peripheral surface, 15h seal groove, 15i seal groove, 16a seal material, 16b seal material, 17 suction check valve assembly, 17a suction check valve, 17b spring, 17d valve passage, 18 pressure regulating valve 20 electric motor, 20a first chamber, 50 relief valve assembly, 50a relief valve, 50 Valve press, 100 Scroll compressor, 200 Air conditioner, 201 Outdoor unit, 202 Indoor unit, 204 Four-way valve, 205 Gas pipe, 206 Indoor heat exchanger, 207 Liquid pipe, 208 Second decompressor, 209 Medium pressure receiver 210, first pressure reducing device, 211 outdoor heat exchanger, 214 gas side valve, 215 liquid side valve, 216 gas side connection part, 217 liquid side connection part, 218 suction pipe, 300 scroll compressor.

Claims (2)

In the sealed container, a compression mechanism unit, an electric motor that drives the compression mechanism unit, and refrigeration oil that lubricates the compression mechanism unit, the inside of the sealed container is a high-pressure scroll compressor,
The compression mechanism is
A fixed scroll in which plate-like spiral teeth are formed on one surface of the base plate portion and the base plate portion;
A plate-like spiral having the same shape as the plate-like spiral teeth of the fixed scroll is provided on one surface of the base plate portion and the base plate, and the compression chamber is combined with the plate-like spiral teeth of the fixed scroll. Forming a swinging scroll;
An Oldham ring to prevent rotation of the orbiting scroll;
A main shaft fixed to the electric motor and driving the orbiting scroll;
A guide frame fixed to the hermetic container, supporting the main shaft in a radial direction and coupled to the fixed scroll.
During the reverse rotation operation of the electric motor, the pressure in the boss space of the orbiting scroll is lower than the pressure in the sealed container, and the refrigeration oil is supplied to the compression mechanism by the differential pressure. The base plate portion of the dynamic scroll is provided with a communication hole for communicating the boss portion space of the swing scroll and the compression chamber of the expansion stroke ,
A scroll check compressor provided with a communication check valve in the communication hole so that refrigerant does not flow from the compression chamber into the boss space through the communication hole during forward rotation of the electric motor. . In the sealed container, a compression mechanism unit, an electric motor that drives the compression mechanism unit, and refrigeration oil that lubricates the compression mechanism unit, the inside of the sealed container is a high-pressure scroll compressor,
The compression mechanism is
A fixed scroll in which plate-like spiral teeth are formed on one surface of the base plate portion and the base plate portion;
A plate-like spiral having the same shape as the plate-like spiral teeth of the fixed scroll is provided on one surface of the base plate portion and the base plate, and the compression chamber is combined with the plate-like spiral teeth of the fixed scroll. Forming a swinging scroll;
An Oldham ring to prevent rotation of the orbiting scroll;
A main shaft fixed to the electric motor and driving the orbiting scroll;
A guide frame fixed to the hermetic container, supporting the main shaft in a radial direction and coupled to the fixed scroll.
During the reverse rotation operation of the electric motor, the pressure in the boss space of the orbiting scroll is lower than the pressure in the sealed container, and the refrigeration oil is supplied to the compression mechanism by the differential pressure. The base plate portion of the dynamic scroll is provided with a communication hole for communicating the boss portion space of the swing scroll and the compression chamber of the expansion stroke ,
The position of the communication hole in the base plate portion of the orbiting scroll is such that the communication hole communicates with the boss space in a predetermined rotation range of one rotation of the main shaft and the motor is rotated forward. A scroll compressor characterized in that the refrigerant in the middle of compression of the compression chamber does not flow into the boss space (a position where the pressure during compression of the compression chamber becomes smaller than the pressure of the boss space) .

Images