JP7580633B2 - Scroll Compressor - Google Patents

Description

The present disclosure relates to a scroll compressor having a compression mechanism.

The scroll compressor includes a compression mechanism that compresses the refrigerant, a rotating shaft, and an electric motor that drives the compression mechanism via the rotating shaft. The compression mechanism includes a fixed scroll and an orbiting scroll, which are arranged opposite each other so that their spiral teeth mesh with each other, and a compression chamber is formed between the spiral teeth. The fixed scroll is fixed inside the pressure vessel. The orbiting scroll has a base plate and a boss, and the spiral teeth are provided on one side of the base plate, and the boss is provided on the back side of the base plate into which the eccentric shaft of the rotation shaft is fitted. The scroll compressor also includes a frame that is fixed inside the pressure vessel and supports the orbiting scroll. In the scroll compressor, the rotating shaft is rotated by the electric motor, so that the orbiting scroll fitted in the eccentric shaft performs an orbital motion, changing the volume of the compression chamber and compressing the refrigerant. In such a compressor, there is a compressor in which a suction port is formed on the outer periphery of the frame to pass the refrigerant sucked from the suction pipe through the compression mechanism (see, for example, Patent Document 1). Generally, in addition to holes for the suction port, a protrusion such as a wall separating the suction port may be formed on the outer periphery of the thrust surface of the frame of a scroll compressor. Such a structure on the outer periphery of the frame is provided on the outer periphery side of the movable range of the base plate so as not to be blocked by the base plate.

Patent No. 6678762

In the scroll compressor of Patent Document 1, the orbiting scroll is configured to perform an orbital motion on the frame so that the center of the movable range of the base plate coincides with the center of the rotation axis, i.e., the center of the frame. That is, in Patent Document 1, non-movable areas, which are areas that do not face the base plate and its movable area, are evenly provided in the circumferential direction on the upper surface of the frame. Therefore, in a configuration in which the center of the movable range of the base plate coincides with the center of the frame as in Patent Document 1, the size of the base plate is limited to avoid the structure such as the suction port provided in a part of the circumferential direction of the frame outer periphery overlapping with the movable range of the base plate of the orbiting scroll, thereby preventing the supply of refrigerant to the compression mechanism. Alternatively, the size of the structure on the outer periphery of the frame is limited by the base plate. If the size of the base plate is limited, the size of the orbiting scroll is limited, so the capacity is reduced, and on the other hand, if the size of the suction port is limited, the suction pressure of the refrigerant is reduced. As a result, it is not possible to provide a scroll compressor with good performance.

This disclosure has been made to solve the problems described above, and aims to provide a scroll compressor with good performance by relaxing the restrictions on the size of the oscillating scroll and the size of the structure on the outer periphery of the frame.

The scroll compressor of the present disclosure comprises a compression mechanism unit having a fixed scroll and an oscillating scroll and compressing a refrigerant, a rotating shaft having an eccentric portion, an electric motor unit driving the compression mechanism unit via the rotating shaft, a pressure vessel in which the compression mechanism unit and the electric motor unit are accommodated, and a frame fixed inside the pressure vessel and supporting the oscillating scroll in an axial direction along which the rotating shaft extends, wherein the oscillating scroll has a oscillating base plate portion, an oscillating spiral tooth provided on a first surface of the oscillating base plate portion facing the fixed scroll, and a boss portion provided on a second surface of the oscillating base plate portion that is the reverse side of the first surface and into which the eccentric portion is fitted, and when viewed in the axial direction, the oscillating base plate portion and the boss portion are arranged so that the position of the center of the oscillating base plate portion is different from the position of the center of the boss portion so that the center of the range of motion of the oscillating base plate portion is eccentric from the center of the frame.

According to the present disclosure, the oscillating platen and the boss are arranged such that the center of the oscillating platen is different from the center of the boss when viewed from the axial direction, so that the center of the movable range of the oscillating platen is eccentric from the center of the frame. Therefore, the non-movable range of the frame is narrower in the eccentric direction, while being wider on the opposite side to the eccentric direction. Therefore, even if a structural part is provided on the opposite side of the eccentric direction of the movable range of the oscillating platen, there is a margin in the non-movable range to enlarge the oscillating platen or to enlarge the structural part. As a result, it is possible to provide a scroll compressor with good performance by relaxing the restrictions on the size of the oscillating scroll and the size of the structure on the outer periphery of the frame.

1 is a vertical cross-sectional view showing a schematic configuration of a compressor according to a first embodiment. 2 is a partially enlarged view showing a peripheral structure of an eccentric shaft in the compressor of FIG. 1 . FIG. 2 is a plan view showing a schematic configuration of a first frame in the compressor of FIG. 1 . 2 is a cross-sectional view taken along the line AA in the compressor of FIG. 1 , showing a schematic positional relationship between the orbiting scroll and the first frame when the orbiting scroll is shifted to the right. FIG. FIG. 5 is a cross-sectional view taken along the line B-B of FIG. 4, showing a schematic positional relationship between the orbiting scroll, the first frame, and the rotating shaft in the compressor. 6 is a vertical cross-sectional view showing a schematic positional relationship between the orbiting scroll, the first frame, and the rotating shaft when the orbiting scroll is shifted to the left in the compressor shown in FIG. 5 . FIG. FIG. 2 is a cross-sectional view that illustrates a first modified example of the compression mechanism of the compressor of FIG. 1 . 1. FIG. 4 is a cross-sectional view showing a schematic diagram of a second modified example of the compression mechanism of the compressor shown in FIG. 1. FIG. 4 is a cross-sectional view showing a schematic diagram of a third modified example of the compression mechanism of the compressor of FIG. FIG. 6 is a partial cross-sectional view illustrating a schematic configuration of a compressor according to a second embodiment. 11 is a cross-sectional view illustrating a schematic positional relationship between the orbiting scroll and the first frame when the orbiting scroll shifts to the right in the compressor according to the second embodiment. FIG. 12 is a vertical cross-sectional view showing a schematic positional relationship between the orbiting scroll, the first frame, and the rotating shaft when the orbiting scroll moves to the left in the compressor shown in FIG. 11 . FIG. 13 is a cross-sectional view illustrating a schematic positional relationship between the orbiting scroll and the first frame when the orbiting scroll shifts to the right in the compressor according to embodiment 3. FIG. 14 is a vertical cross-sectional view showing a schematic positional relationship between the orbiting scroll, the first frame, and the rotating shaft when the orbiting scroll moves to the left in the compressor shown in FIG. 13.

Hereinafter, an embodiment of the present disclosure will be described based on the drawings. Note that the present disclosure is not limited to the embodiments described below. In addition, the size relationship of each component in the following drawings may differ from the actual one. In addition, in the following description, terms indicating directions (e.g., "upper", "lower", "left", "right", "front", "rear", etc.) are used as appropriate to facilitate understanding, but these terms are for the purpose of explanation and do not limit the present disclosure. Unless otherwise specified, these terms indicating directions refer to the direction in which the scroll compressor is viewed from the front side (front side) with the direction in which the rotating shaft 33 of the scroll compressor extends (axial direction) as the height direction, and FIG. 1 shows a vertical cross-sectional view of the scroll compressor viewed from the front side. In each figure, the same reference numerals are assigned to the same or equivalent parts, and this is common throughout the entire specification. In the following description, the scroll compressor may be simply referred to as a compressor.

Embodiment 1.
Fig. 1 is a vertical cross-sectional view showing a schematic configuration of a compressor 100 according to a first embodiment. In Fig. 1, the direction of the arrow X indicates the width direction of the compressor 100, the direction of the arrow Y indicates the depth direction of the compressor 100, and the direction of the arrow Z indicates the height direction of the compressor 100. Fig. 2 is a partially enlarged view showing a peripheral structure of an eccentric shaft in the compressor 100 of Fig. 1. Fig. 3 is a plan view showing a schematic configuration of a first frame 46 in the compressor 100 of Fig. 1. The configuration of the compressor 100 will be described below with reference to Figs. 1 to 3.

The compressor 100 is one of the components of a refrigeration cycle device, such as a freezer, a refrigerator, an air conditioner, a water heater, or a vending machine. The compressor 100 is a fluid machine that draws in the refrigerant circulating in the refrigeration cycle, compresses the drawn refrigerant, and discharges it.

1, the compressor 100 includes a compression mechanism 10 that compresses a refrigerant, a rotating shaft 33, an electric motor 30 that drives the compression mechanism 10 via the rotating shaft 33, and a pressure vessel 40 that houses the compression mechanism 10 and the electric motor 30. The compressor 100 also includes a first frame 46 that supports the compression mechanism 10 in the axial direction.

Inside the compression mechanism 10, a compression chamber 11 whose volume changes with the rotation of the rotating shaft 33 is formed, and the refrigerant is compressed in the compression chamber 11. In addition, the compression mechanism 10 is formed with a discharge port 3 that discharges the refrigerant compressed in the compression chamber 11 to the outside of the compression mechanism 10 in the pressure vessel 40. The pressure vessel 40 has, for example, a cylindrical body vessel 42, an upper vessel 41 welded to the upper opening of the body vessel 42, and a lower vessel 43 welded to the lower opening of the body vessel 42. In addition, the pressure vessel 40 is connected to a suction pipe 44 that draws the external refrigerant into the pressure vessel 40, and a discharge pipe 45 that discharges the refrigerant compressed in the compression mechanism 10 to the outside of the pressure vessel 40. The compression mechanism 10 is configured to compress the gas refrigerant drawn from the suction pipe 44 in the compression chamber 11 and discharge it through the discharge port 3 to the outside of the compression mechanism 10 in the pressure vessel 40 by being driven by the electric motor 30. The compression mechanism 10 has a fixed scroll 21 and an orbiting scroll 22. The first frame 46 supports the orbiting scroll 22 of the compression mechanism 10.

In the example shown in FIG. 1, the electric motor unit 30 is disposed at the bottom of the pressure vessel 40, the compression mechanism unit 10 is disposed at the top of the pressure vessel 40, the fixed scroll 21 constitutes the top of the compression mechanism unit 10, and the swing scroll 22 constitutes the bottom of the compression mechanism unit 10. The first frame 46 is disposed below the swing scroll 22, and the discharge port 3 is formed at the top of the fixed scroll 21. In the example shown in FIG. 1, the intake pipe 44 is provided on the right side of the body vessel 42 of the pressure vessel 40, and the discharge pipe 45 is provided in the upper vessel 41 of the pressure vessel 40. The intake pipe 44 is provided so as to communicate with the space below the first frame 46. In addition, an oil reservoir for storing lubricating oil is provided at the bottom of the pressure vessel 40.

The compressor 100 also includes a chamber 4 disposed above the fixed scroll 21 in the pressure vessel 40. A recessed portion 4a is formed on the lower surface of the chamber 4, and the refrigerant discharged from the discharge port 3 of the compression mechanism 10 is temporarily stored in the recessed portion 4a. A chamber discharge port 4b extending in the height direction (arrow Z direction) is formed in the center of the recessed portion 4a. The discharge port 3 of the compression mechanism 10 and the recessed portion 4a of the chamber 4 are connected, and the recessed portion 4a of the chamber 4 and the chamber discharge port 4b are connected. As a result, the refrigerant compressed in the compression chamber 11 of the compression mechanism 10 is discharged into the space above the compression mechanism 10 in the pressure vessel 40 through the discharge port 3, the recessed portion 4a of the chamber 4, and the chamber discharge port 4b.

In the following description, the space within the pressure vessel 40 above the fixed scroll 21 will be referred to as the discharge space So, and the space below the first frame 46 in which the electric motor section 30 is provided will be referred to as the motor space Sm.

The compressor 100 also includes a discharge valve 5a and a valve retainer 5b disposed on the chamber 4. One end of the discharge valve 5a and the valve retainer 5b is fixed to the chamber 4 by a fixing member 5c formed of, for example, a bolt. Hereinafter, the discharge valve 5a, the valve retainer 5b, and the fixing member 5c are collectively referred to as the discharge valve mechanism 5.

The discharge port 3 formed in the fixed scroll 21 is formed in the approximate center of the fixed base plate portion 23, and the gas refrigerant compressed in the compression chamber 11 to high pressure is discharged from the discharge port 3. The discharge valve mechanism 5 installed on the fixed scroll 21 is installed on the outlet side surface (in this embodiment, the upper surface) of the discharge port 3 in the fixed base plate portion 23, and is configured to open and close the discharge port 3 according to the discharge pressure of the refrigerant and prevent backflow of the refrigerant.

The fixed scroll 21 has a fixed base plate portion 23 and a fixed spiral tooth 25, which is a protrusion of an involute curve shape erected on one surface (the lower surface in FIG. 1) of the fixed base plate portion 23. The fixed scroll 21 is fixed to the inner wall surface of the pressure vessel 40 by shrink fitting, welding, or the like. Specifically, a step (not shown) is provided on the inner wall surface of the body vessel 42 of the pressure vessel 40, and the outer peripheral edge portion of the fixed base plate portion 23 is fitted into and joined to the step.

The swing scroll 22 has a swing table portion 24 and a swing spiral tooth 26, which is a protrusion of an involute curve shape erected on one surface (the upper surface in the example of FIG. 1) of the swing table portion 24. The swing scroll 22 is supported rotatably by the first frame 46. A cylindrical boss portion 27 is provided on the other surface of the swing table portion 24. An eccentric shaft portion 33a of the rotating shaft 33 described later is fitted into the boss portion 27. In the compressor 100 of the present disclosure, as shown in FIG. 2, the center line 53 of the boss portion 27 and the center line 54 of the swing table portion 24 are configured not to be on the same vertical line. The center line 53 of the boss portion 27 shown in FIG. 2 coincides with the center line Ax2 of the eccentric shaft portion 33a shown in FIG. 1. 1, the center line 53 of the boss portion 27 is omitted, and the center line Ax2 of the eccentric shaft portion 33a is omitted in Fig. 2. Hereinafter, the eccentric shaft portion 33a may be referred to as the eccentric portion of the rotating shaft 33.

2, a first Oldham groove 24a is formed at an outer position of the boss portion 27 on the other surface (lower surface) of the oscillating base plate portion 24. An upper surface protrusion 29b of an Oldham ring 29 described later is arranged in the first Oldham groove 24a, and the first Oldham groove 24a is configured to guide the upper surface protrusion 29b of the Oldham ring 29. The first Oldham groove 24a is long in the radial direction and is, for example, an oval groove when viewed in the axial direction. A pair of first Oldham grooves 24a are provided facing each other.

The orbiting scroll 22 revolves around the eccentric shaft portion 33a while its rotational motion is restricted by the Oldham ring 29 relative to the fixed scroll 21. In other words, the orbiting scroll 22 performs an orbital rotation motion (so-called rocking motion).

As shown in Figure 1, the fixed scroll 21 and the oscillating scroll 22 are fitted together so that the fixed spiral teeth 25 and the oscillating spiral teeth 26 mesh with each other, and are mounted in a pressure vessel 40. The compression chamber 11 described above is formed between the fixed spiral teeth 25 and the oscillating spiral teeth 26. When the oscillating scroll 22 oscillates in the pressure vessel 40, the relative positional relationship between the fixed spiral teeth 25 and the oscillating spiral teeth 26 changes, thereby changing the volume of the compression chamber 11 and compressing the refrigerant in the compression chamber 11.

Although the fixed scroll 21 is defined as being directly fixed to the pressure vessel 40, this is not particularly limited. The first frame 46 supporting the orbiting scroll 22 may have an outer wall that is screwed to the fixed base plate portion 23 of the fixed scroll 21, and the fixed scroll 21 may be fixed to the pressure vessel 40 via the outer wall of the first frame 46.

However, when the fixed scroll 21 is directly fixed to the pressure vessel 40, there is no need to provide an outer wall on the first frame 46 that extends toward the side of the fixed scroll 21, i.e., toward the upper side, so the space between the outer periphery of the swing scroll 22 and the inner wall surface of the body vessel 42 becomes wider. Therefore, in a configuration in which the fixed scroll 21 is directly fixed to the pressure vessel 40, the size of the swing scroll 22 is not restricted by the outer wall, and the outer diameter of the swing table portion 24 and the winding diameter of the swing spiral tooth 26 can be increased. In this case, the maximum refrigeration capacity of the compressor 100 can be increased without changing the diameter of the body vessel 42. In addition, it is also possible to design the compressor 100 so as to reduce the thrust load by increasing the size of the swing table portion 24. Alternatively, in a configuration in which the fixed scroll 21 is directly fixed to the pressure vessel 40, if the size of the swing scroll 22 is not changed, the diameter of the body vessel 42 can be reduced. In this case, the compressor 100 can be made smaller without reducing the maximum refrigeration capacity.

The first frame 46 is made of, for example, an iron-based magnetic material. A thrust plate 46s is provided on the upper surface of the first frame 46 in a portion facing the oscillating base plate portion 24. The thrust plate 46s supports the oscillating scroll 22 so that it can slide freely. That is, when the oscillating scroll 22 performs an orbital revolution, the lower surface of the oscillating scroll 22 slides on the thrust plate 46s of the first frame 46.

2 and 3, a boss accommodating portion 46f is provided in the center of the first frame 46, in which the boss portion 27 of the orbiting scroll 22 is accommodated. A bearing portion 46b that protrudes toward the inner periphery and rotatably holds the rotating shaft 33 is provided in the lower portion of the boss accommodating portion 46f in the first frame 46. An Oldham accommodating portion 46o with an expanded inner diameter is formed in the upper portion of the boss accommodating portion 46f in the first frame 46, and the ring portion 29r (see FIG. 2) of the Oldham ring 29 described later is accommodated in the Oldham accommodating portion 46o. As shown in FIG. 3, a second Oldham groove 46o1 is formed in the bottom surface of the Oldham accommodating portion 46o of the first frame 46. A lower surface protrusion (not shown) of the Oldham ring 29 is arranged in the second Oldham groove 46o1 of the first frame 46, and the second Oldham groove 46o1 is configured to guide the lower surface protrusion of the Oldham ring 29. The second Oldham grooves 46o1 extend in the radial direction and are provided in pairs facing each other. In Fig. 3, a line connecting the pair of second Oldham grooves 46o1 of the first frame 46 is shown by a dashed line, and a line connecting the pair of first Oldham grooves 24a of the oscillating bed portion 24 shown in Fig. 2 is shown by a dashed line. These lines are perpendicular to each other.

1, in order to supply the refrigerant sucked from the suction pipe 44 to the compression chamber 11, a suction port 46a penetrates from the motor space Sm below the first frame 46 to the surface facing the orbiting scroll 22. As shown in FIG. 1, the suction port 46a is arranged in the opposite phase to the suction pipe 44 across the rotating shaft 33.

As shown in FIG. 1, the electric motor unit 30 has a stator 31 fixed to the pressure vessel 40 and a rotor 32 arranged on the inner periphery of the stator 31. The rotor 32 is rotatably attached to the stator 31 and is rotated by passing electricity through the stator 31. A rotating shaft 33 is attached to the center of the rotor 32, and the rotating shaft 33 rotates when the rotor 32 is rotated. An eccentric shaft portion 33a is formed at the upper end of the rotating shaft 33, which rotatably fits into the boss portion 27 of the orbiting scroll 22. The electric motor unit 30 drives the orbiting scroll 22 via the rotating shaft 33, thereby compressing the gas refrigerant in the compression mechanism unit 10.

A second frame 47 is fixed below the electric motor section 30 inside the pressure vessel 40. A ball bearing 48 is press-fitted and fixed in the center of the second frame 47. The second frame 47 supports the ball bearing 48 inside the pressure vessel 40. The second frame 47 supports the lower end of the rotating shaft 33 so that it can rotate freely by means of the ball bearing 48.

The rotating shaft 33 is a rod-shaped member made of metal. The rotating shaft 33 includes a main shaft portion 33b constituting the main portion of the rotating shaft 33, and an eccentric shaft portion 33a constituting the upper end portion of the rotating shaft 33. The main shaft portion 33b of the rotating shaft 33 is arranged so that its center line Ax1 coincides with the center axis of the body container 42. The main shaft portion 33b is fixed to the central through hole of the rotor 32 of the electric motor portion 30 by shrink fitting or the like, and is rotatably supported by a bearing portion 46b provided in the center of the first frame 46 and a ball bearing 48 provided in the center of the second frame 47.

The eccentric shaft portion 33a of the rotating shaft 33 is provided so that its center line Ax2 is eccentric with respect to the center line Ax1 of the main shaft portion 33b. The eccentric shaft portion 33a is fitted into the boss portion 27 of the orbiting scroll 22 and is rotatably held by the boss portion 27. The rotating shaft 33 rotates with the rotation of the rotor 32 of the electric motor portion 30, and the eccentric shaft portion 33a orbits the orbiting scroll 22. In addition, an oil passage 33c is provided vertically penetrating the inside of the main shaft portion 33b and the eccentric shaft portion 33a, and as the rotating shaft 33 rotates, the lubricating oil sucked up from the oil reservoir is supplied between parts that come into mechanical contact with each other, such as the compression mechanism portion 10.

The compressor 100 also includes an Oldham ring 29 that restricts the rotation of the orbiting scroll 22, and a bush 28 that connects the orbiting scroll 22 and the eccentric shaft portion 33a. The configurations of the Oldham ring 29 and the bush 28 will be described with reference to Figure 2. The bush 28 is attached to the outer periphery of the eccentric shaft portion 33a of the rotating shaft 33 and is disposed in the boss accommodating portion 46f of the first frame 46. The Oldham ring 29 is disposed on the outer periphery of the bush 28 and is disposed in the Oldham accommodating portion 46o of the first frame 46.

The Oldham ring 29 includes a ring portion 29r, two upper projections 29b provided on the upper surface of the ring portion 29r, and two lower projections (not shown) provided on the lower surface of the ring portion 29r. The two upper projections 29b are provided at positions facing each other on the ring portion 29r, and the two lower projections are also provided at positions facing each other on the ring portion 29r.

When the orbiting scroll 22 revolves due to the rotation of the rotating shaft 33, the upper surface protrusion 29b slides in the first Oldham groove 24a of the oscillating base plate portion 24, and the lower surface protrusion slides in the second Oldham groove 46o1 of the first frame 46, with the range of movement being restricted by the inner wall of the groove. With this configuration, the orbiting scroll 22 does not rotate on its axis.

The bush 28 is made of, for example, a metal such as iron. The bush 28 has, for example, a slider 28a and a balance weight 28b. The slider 28a is a cylindrical member with a flange, and the cylindrical portion of the slider 28a is disposed on the inner periphery of the boss portion 27 of the swing scroll 22 and is fitted into each of the eccentric shaft portion 33a and the boss portion 27. The balance weight 28b is a member having a donut-shaped shape when viewed from the axial direction. The balance weight 28b is fitted to the flange of the slider 28a by a method such as shrink fitting. The balance weight 28b has a weight portion 28b1 having an approximately C-shaped shape when viewed from the axial direction. In the example shown in FIG. 2, the weight portion 28b1 is provided only on the left side of the balance weight 28b. The balance weight 28 b has a weight portion 28 b 1 that is provided only on a portion of the circumferential direction, thereby offsetting the centrifugal force of the orbiting scroll 22 .

Next, the operation of the compressor 100 will be described based on FIG. 1. In the compressor 100, when the stator 31 of the motor unit 30 is energized, the rotor 32 and the rotating shaft 33 attached to the rotor 32 rotate. When the rotating shaft 33 rotates, the swing scroll 22 attached to the eccentric shaft portion 33a of the rotating shaft 33 via the bush 28 swings relative to the fixed scroll 21. As a result, the volume of the compression chamber 11 formed between the fixed spiral teeth 25 of the fixed scroll 21 and the swing spiral teeth 26 of the swing scroll 22 varies continuously. At this time, when the volume of the compression chamber 11 increases, the pressure in the compression chamber 11 falls below the pressure in the suction space (in the example shown in FIG. 1, the motor space Sm) in the pressure vessel 40, and the refrigerant in the suction space is sucked into the compression chamber 11 through the suction port 46a.

Here, as shown in FIG. 1, in the first frame 46, when the suction port 46a is provided on the side (e.g., the half to the left of the center line Ax1 of the main shaft portion 33b) opposite to the side where the suction pipe 44 is provided with respect to the center line Ax1 of the main shaft portion 33b, i.e., the center of the first frame 46, the refrigerant can cool the motor portion 30 by entering the motor space Sm from the suction pipe 44 and being sucked into the compression chamber 11.

Thereafter, as the volume of the compression chamber 11 decreases due to the oscillating motion of the oscillating scroll 22, the refrigerant sucked into the compression chamber 11 is compressed, and the pressure in the compression chamber 11 increases. When the pressure in the compression chamber 11 exceeds a preset pressure, the compressed refrigerant pushes up the discharge valve 5a of the discharge valve mechanism 20 and is discharged outside the pressure vessel 40 (for example, to the condenser of the refrigeration cycle) through the discharge space So and the discharge pipe 45.

Figure 4 is an A-A cross-sectional view showing the positional relationship between the orbiting scroll 22 and the first frame 46 when the orbiting scroll 22 is shifted to the right in the compressor 100 of Figure 1. Also, in Figure 4, the fixed scroll teeth 25 are shown by a dashed two-dot line. Figure 5 is a B-B cross-sectional view showing the positional relationship between the orbiting scroll 22, the first frame 46, and the rotating shaft 33 in the compressor 100 of Figure 4. Figure 6 is a vertical cross-sectional view showing the positional relationship between the orbiting scroll 22, the first frame 46, and the rotating shaft 33 in the compressor 100 of Figure 5 when the orbiting scroll 22 is shifted to the left. In Figures 5 and 6, the bush 28 and Oldham ring 29 shown in Figure 1 are omitted for ease of explanation.

The movable range R1 and non-movable range R2 of the oscillating platen portion 24 on the first frame 46 will be described below with reference to Figures 4 to 6. The movable range R1 and non-movable range R2 are obtained by dividing a cylindrical space formed in the space inside the body container 42 above the first frame 46 and outside the oscillating platen portion 24. As shown in Figure 4, the movable range R1 is a region through which the oscillating platen portion 24 moves when the oscillating scroll 22 performs an orbital revolution on the first frame 46, and has a cylindrical shape. On the other hand, the non-movable range R2 is a region that is provided outside the boundary 50 of the movable range R1, into which the oscillating platen portion 24 does not enter, and has a cylindrical shape.

5 and 6, in the present disclosure, the center line 53 of the boss portion 27 and the center line 54 of the oscillating base plate portion 24 in the oscillating scroll 22 are configured not to be on the same straight line in the vertical direction (arrow Z direction). In other words, the oscillating scroll 22 performs an oscillating motion in a state in which the center line 54 of the oscillating base plate portion 24 is further eccentric with respect to the center line Ax2 (see FIG. 1) of the eccentric shaft portion 33a that is eccentric from the main shaft portion 33b.

With this configuration, as viewed from the axial direction as shown in Figure 4, the center line 51 of the movable range R1 of the oscillating table portion 24 while the oscillating scroll 22 is performing an oscillating motion is eccentric from the center line Ax1 (see Figure 1) of the main shaft portion 33b, i.e., the center line 52 of the first frame 46. Therefore, on the first frame 46, the non-movable range R2 of the oscillating table portion 24 has a cylindrical shape whose radial width is not uniform in the circumferential direction. More specifically, in the non-movable range R2, the radial width is narrower in the eccentric direction of the center line 51 of the movable range R1, and the radial width is wider on the opposite side to the eccentric direction.

In the example shown in Figure 4, the center line 51 of the movable range R1 of the oscillating base plate portion 24 on the first frame 46 is offset from the center line 52 of the first frame 46 to the right side where the suction pipe 44 is provided. In the non-movable range R2, the radial width is wider on the left side of the non-movable range R2 than on the right side, the rear side, or the front side.

The size of the oscillating platen 24 is set so that the oscillating scroll 22 does not cover the suction port 46a. In order to easily ensure the size of the suction port 46a, in the example shown in FIG. 4, the suction port 46a is provided on the opposite side of the eccentric direction of the center line 51 of the movable range R1 of the oscillating platen 24 in the first frame 46, i.e., in the left half of the first frame 46. Also, in the example shown in FIG. 4, only one arc-shaped suction port 46a is provided in the first frame 46.

As can be seen from the boundary 50 of the movable range R1 shown in Figure 4, the oscillating base plate portion 24 does not overlap with the suction port 46a at any timing during the oscillating motion of the oscillating scroll 22. Even in the state in which the oscillating scroll 22 has oscillated most toward the suction port 46a (to the left in Figure 6) in the width direction (arrow X direction) as shown in Figure 6, the oscillating scroll 22 is not positioned above the suction port 46a.

In the example shown in FIG. 4, the end 26e of the oscillating scroll 22 is located at 45° forward from the suction pipe 44. The fixed scroll 25 shown by the dashed line in FIG. 4 has a symmetrical spiral shape with the oscillating scroll 26, and the end 25e of the fixed scroll 25 is located at 180° from the end 26e of the oscillating scroll 26. That is, in the example shown in FIG. 4, the end 25e of the fixed scroll 25 is located at 135° backward from the suction pipe 44. Then, refrigerant flows into the compression chamber 11 from the suction port 46a provided in the first frame 46 through the gap between the end 26e of the oscillating scroll 26 and the fixed scroll 25, or the gap between the end 25e of the fixed scroll 25 and the oscillating scroll 26. Hereinafter, these gaps that serve as the inlets of the refrigerant to the compression chamber 11 may be referred to as the compression chamber inlet 11a. In the example shown in FIG. 4, the compression chamber inlets 11a are provided at two locations, approximately 135° forward and approximately 45° rearward from the circumferential center position Lp of the suction port 46a. The front compression chamber inlet 11a opens to the left, and the rear compression chamber inlet 11a opens to the right. In addition, in the example shown in FIG. 4, the arc-shaped suction port 46a is provided on the left side of the first frame 46 in an angle range of 90° from 45° forward to 45° rearward. Note that the positions of the winding end portions 25e and 26e in the circumferential direction, the arrangement of the compression chamber inlet 11a, and the angle range of the suction port 46a are not limited to the above case. Modified examples will be described later.

In addition, in the present disclosure, since the center line 51 of the movable range R1 is eccentric, the position of the start of the fixed spiral tooth 25 is also eccentric from the center of the fixed base plate portion 23 when viewed from the axial direction so that the oscillating spiral tooth 26 and the fixed spiral tooth 25 mesh. Specifically, the position of the start of the fixed spiral tooth 25 is configured to be shifted in the same direction as the eccentric direction of the center line 51 of the movable range R1 of the oscillating base plate portion 24 with respect to the center of the fixed base plate portion 23 when viewed from the axial direction. Therefore, the position of the start of the fixed spiral tooth 25 is eccentric from the center line Ax1 of the main shaft portion 33b shown in FIG. 1 and the center line 52 of the first frame 46 shown in FIG. 4 in the same direction as the eccentric direction of the center line 51 of the movable range R1 of the oscillating base plate portion 24 when viewed from the axial direction. In addition, since the position of the start of the winding of the fixed spiral tooth 25 is eccentric from the center of the fixed base plate portion 23 when viewed from the axial direction, the discharge port 3 of the fixed base plate portion 23 shown in Figure 1 is also eccentric in the same manner as the position of the start of the winding.

In this way, by arranging the oscillating base plate portion 24 and the boss portion 27 so that the center of the oscillating base plate portion 24 and the center of the boss portion 27 are different, the oscillating spiral tooth 26 is also shifted in an eccentric direction more than in conventional compressors, and as a result, the fixed spiral tooth 25 and the discharge port 3 of the fixed scroll 21 are also positioned at positions shifted from the center of the fixed base plate portion 23 and the center of the body container 42.

Incidentally, when the center line 53 of the boss portion 27 and the center line 54 of the oscillating base plate portion 24 are in the same position as viewed in the axial direction as in the conventional case, the center line 51 of the movable range R1 of the oscillating base plate portion 24 while the oscillating scroll 22 is performing an oscillating motion coincides with the center line 52 of the first frame 46. Therefore, in the conventional configuration, the radial width of the non-movable range R2 is uniform in the circumferential direction and is smaller than the maximum radial width Wmax of the non-movable range R2 in the present disclosure.

In the present disclosure, as shown in FIG. 4, the center line 51 of the movable range R1 of the oscillating base plate portion 24 on the first frame 46 is eccentric from the center line 52 of the first frame 46, so that the maximum radial width Wmax of the non-movable range R2 can be made larger than in the past. Therefore, the space inside the body container 42 can be effectively utilized. For example, if the inner diameter of the body container 42 and the diameter of the movable range R1 of the oscillating base plate portion 24 are each the same as in the past, the area of the suction port 46a can be enlarged. In this case, the suction pressure loss of the refrigerant can be suppressed more than in the past, so the efficiency of the compressor 100 can be improved.

In addition, for example, if the inner diameter of the body container 42 and the area of the suction port 46a are the same as in the conventional case, the diameter of the movable range R1 of the oscillating table portion 24 on the first frame 46 can be increased, or the diameter of the oscillating table portion 24 can be increased. In this case, the capacity can be increased without changing the size of the compressor 100, and the efficiency of the compressor 100 can be improved.

In addition, in the present disclosure, the advantages are not lost when the fixed scroll 21 is directly fixed to the pressure vessel 40, i.e., when the first frame 46 does not have an outer wall to which the fixed base plate portion 23 of the fixed scroll 21 is screwed. As shown in FIG. 5, in the eccentric direction of the center line 51 of the range of motion R1 of the oscillating base plate portion 24, the range of motion R1 of the oscillating base plate portion 24 can be expanded to the vicinity of the inner wall surface of the body vessel 42.

In addition, as shown in the example of Figure 2, a weight portion 28b1 is provided on the bush 28 attached to the boss portion 27 of the oscillating scroll 22, and this weight portion 28b1 is positioned on the opposite side of the eccentricity direction of the center line 51 of the movable range R1, thereby making it possible to suppress vibration during oscillating motion due to eccentricity.

Figure 7 is a cross-sectional view showing a first modified example of the compression mechanism 10 of the compressor 100 of Figure 1. Based on Figure 7, the positional relationship between the fixed spiral teeth 25 and the oscillating spiral teeth 26 in the first modified example will be described.

In the first modified example shown in Figure 7, the fixed spiral tooth 25 and the oscillating spiral tooth 26 have symmetrical spiral shapes, as in the case shown in Figure 4. However, in the first modified example, the end portion 26e of the oscillating spiral tooth 26 is positioned 180° from the end portion 25e of the fixed spiral tooth 25. Also, in the first modified example, the arrangement of the compression chamber inlet 11a in the circumferential direction differs from that shown in Figure 4.

Specifically, in the first modified example, the end 26e of the oscillating spiral tooth 26 is located at the rear of the oscillating base plate portion 24, and the end 25e of the fixed spiral tooth 25 is located at the front. The compression chamber inlets 11a are formed at two positions, approximately 90° forward and approximately 90° backward from the circumferential center position Lp of the suction port 46a. The compression chamber inlet 11a on the front side opens to the left, and the compression chamber inlet 11a on the rear side opens to the right.

By making the distances from the suction port 46a to the two compression chamber inlets 11a equal as in the first modified example, the refrigerant from the suction port 46a can be evenly sucked into the compression chamber 11 by the oscillating spiral teeth 26 and the fixed spiral teeth 25. In this case, efficiency is improved compared to a configuration in which only one of the end portions 25e and 26e is located near the suction port 46a.

8 is a cross-sectional view showing a second modified example of the compression mechanism 10 of the compressor 100 of FIG. 1. In the second modified example shown in FIG. 8, the fixed spiral tooth 25 and the oscillating spiral tooth 26 have symmetrical spiral shapes, as in the first modified example shown in FIG. 7, and the end portion 26e of the oscillating spiral tooth 26 is arranged at a position 180° from the end portion 25e of the fixed spiral tooth 25. However, in the second modified example, the arrangement of the compression chamber inlet 11a in the circumferential direction is different from that in the first modified example. Specifically, in the second modified example, the compression chamber inlet 11a facing the opposite direction to the suction port 46a, that is, the right-facing compression chamber inlet 11a, is arranged so as to be closer to the suction port 46a than the left-facing compression chamber inlet 11a. Therefore, the fixed spiral tooth 25 and the oscillating spiral tooth 26 are arranged at a position rotated by an angle θ (for example, 30°) in the circumferential direction from the position shown in FIG. 7. In the example shown in Fig. 8, compression chamber inlets 11a are provided at two locations, approximately 120° forward and approximately 60° backward, from the circumferential center position Lp of suction port 46a shown in Fig. 7. Therefore, the compression chamber inlet 11a facing right and located on the far side has a shorter linear distance from suction port 46a (see Fig. 7) than the compression chamber inlet 11a facing left and located on the near side.

Even if the straight-line distance from the suction port 46a is the same between the right-facing compression chamber inlet 11a and the left-facing compression chamber inlet 11a as in the first modified example, the refrigerant must actually go around the right-facing compression chamber inlet 11a, making it more difficult to enter. In contrast, by changing the straight-line distance from the suction port 46a depending on the direction of the compression chamber inlet 11a as in the second modified example, the refrigerant can be sucked into the compression chamber 11 evenly from the two compression chamber inlets 11a compared to the first modified example. The angle θ at which the fixed spiral teeth 25 and the oscillating spiral teeth 26 are inclined in the circumferential direction is not limited to the above case, but is preferably within a rotation range that is greater than 0° and less than 30°.

Figure 9 is a cross-sectional view showing a schematic diagram of a third modified example of the compression mechanism 10 of the compressor 100 of Figure 1. Based on Figure 9, the positional relationship between the fixed spiral teeth 25 and the oscillating spiral teeth 26 in the third modified example will be described.

In the third modified example shown in Fig. 9, the oscillating spiral tooth 26 and the fixed spiral tooth 25 are arranged so that the compression chamber entrance 11a is located near the suction port 46a, and the position of the end 26e of the oscillating spiral tooth 26 and the position of the end 25e of the fixed spiral tooth 25 are the same in the circumferential direction. In the third modified example, the length of each turn of the oscillating spiral tooth 26 and the fixed spiral tooth 25 is determined so that the compression chamber entrance 11a is located within the angular range in which the arc-shaped suction port 46a is provided in the circumferential direction.

In the example shown in Figure 9, the end portion 26e of the oscillating spiral tooth 26 and the end portion 25e of the fixed spiral tooth 25 are each positioned circumferentially at approximately the same position as the circumferential center position Lp of the intake port 46a, and the compression chamber inlet 11a is configured to open to the rear side.

In this way, both the end 26e of the oscillating spiral tooth 26 and the end 25e of the fixed spiral tooth 25 are positioned in the circumferential direction at the position where the suction port 46a is provided, so that the compression chamber inlet 11a can be provided near the suction port 46a. Therefore, the oscillating spiral tooth 26 and the fixed spiral tooth 25 can more efficiently introduce the refrigerant sucked from the suction port 46a into the compression chamber 11, leading to improved refrigerant supply.

In the third modified example, the position of the compression chamber inlet 11a in the circumferential direction is not limited to the same position as the circumferential center position Lp of the suction port 46a, but may be any position on the radial side of the suction port 46a. For example, the compression chamber inlet 11a is located on the left side in the left-right direction. In other words, in the circumferential angular position, the compression chamber inlet 11a formed by the end portion 26e of the oscillating spiral tooth 26 and the end portion 25e of the fixed spiral tooth 25 may be located in the section between 90° forward and 90° backward from the circumferential center position Lp of the suction port 46a.

As described above, the scroll compressor according to the first embodiment includes a compression mechanism 10 that compresses a refrigerant, a rotating shaft 33 having an eccentric shaft portion 33a, and an electric motor portion 30 that drives the compression mechanism 10 via the rotating shaft 33. The compression mechanism 10 includes a fixed scroll 21 and an oscillating scroll 22. The scroll compressor also includes a pressure vessel 40 in which the compression mechanism 10 and the electric motor portion 30 are housed, and a frame (first frame 46) that is fixed inside the pressure vessel 40 and supports the oscillating scroll 22 in the axial direction in which the rotating shaft 33 extends. The oscillating scroll 22 includes an oscillating table plate portion 24, an oscillating spiral tooth 26 provided on a first surface of the oscillating table plate portion 24 on the side of the fixed scroll 21, and a boss portion 27 provided on a second surface of the oscillating table plate portion 24 that is the back surface of the first surface, into which the eccentric shaft portion 33a is fitted. When viewed from the axial direction, the oscillating plate portion 24 and the boss portion 27 are provided such that the position of a center line 54 of the oscillating plate portion 24 is different from the position of a center line 53 of the boss portion 27 .

This results in a configuration in which the center of the oscillating platen portion 24 and the center of the boss portion 27 do not exist on the same vertical line (arrow Z direction). Therefore, the center line 51 of the movable range R1 of the oscillating platen portion 24 is eccentric from the center line 52 of the first frame. Therefore, the non-movable range R2 in the first frame 46 is narrower in the eccentric direction, while being wider on the opposite side to the eccentric direction. Therefore, even if a structural part is provided on the opposite side of the eccentric direction of the movable range R1 of the oscillating platen portion 24 in the first frame 46, there is a margin in the non-movable range R2 to make the oscillating platen portion 24 larger or to make the structural part larger. As a result, it is possible to relax the restrictions on the size of the oscillating scroll 22 and the size of the structure on the outer periphery of the first frame 46, and to provide a scroll compressor with good performance.

In addition, when viewed from the axial direction, a suction port 46a that supplies refrigerant to the compression mechanism 10 is formed in a non-movable range R2 of the oscillating base plate portion 24 of the frame (first frame 46), which is located on the outer periphery of the movable range R1. By providing the suction port 46a in the non-movable range R2, it is possible to supply refrigerant to the compression chamber 11 while avoiding pressure loss due to the oscillating base plate portion 24.

In addition, when viewed from the axial direction, the suction port 46a is formed on the opposite side to the eccentric direction of the center line 51 of the movable range R1 of the oscillating base plate portion 24 in the frame (first frame 46). This allows the suction port 46a to be larger than before, increasing the amount of refrigerant that can be supplied to the compression chamber 11.

The fixed scroll 21 also has a fixed base plate portion 23 and fixed spiral teeth 25 provided on the surface of the fixed base plate portion 23 facing the oscillating scroll 22. When viewed from the axial direction, the two compression chamber inlets 11a formed by the oscillating spiral teeth 26 and the fixed spiral teeth 25 are arranged so that their linear distances from the suction port 46a are equal.

This allows the refrigerant from the suction port 46a to be evenly sucked into the compression chamber 11 by the oscillating spiral teeth 26 and the fixed spiral teeth 25. In this case, efficiency is improved compared to a configuration in which only one of the end portions 25e and 26e is located near the suction port 46a.

The fixed scroll 21 also has a fixed base plate portion 23 and fixed spiral teeth 25 provided on the surface of the fixed base plate portion 23 facing the oscillating scroll 22. When viewed from the axial direction, the two compression chamber inlets 11a formed by the oscillating spiral teeth 26 and the fixed spiral teeth 25 face one toward the suction port 46a and the other toward the opposite side to the suction port 46a, and the linear distance between the other and the suction port 46a is closer than the linear distance between the one and the suction port 46a. This allows the refrigerant to be evenly sucked into the compression chamber 11 by the oscillating spiral teeth 26 and the fixed spiral teeth 25 regardless of the orientation of the compression chamber inlet 11a.

The fixed scroll 21 also has a fixed base plate portion 23 and a fixed spiral tooth 25 provided on the surface of the fixed base plate portion 23 facing the oscillating scroll 22. The oscillating spiral tooth 26 and the fixed spiral tooth 25 are provided so that one (oscillating spiral tooth 26 in the example of FIG. 9) is longer than the other so that the end portions 25e and 26e are located at the same position in the circumferential direction. The compression chamber inlet 11a formed by the oscillating spiral tooth 26 and the fixed spiral tooth 25 is provided on the side of the suction port 46a in the radial direction. This allows the compression chamber inlet 11a to be provided near the suction port 46a, so that the oscillating spiral tooth 26 and the fixed spiral tooth 25 can more efficiently introduce the refrigerant sucked from the suction port 46a into the compression chamber 11, leading to improved refrigerant supply.

In addition, the fixed scroll 21 is fixed directly to the pressure vessel 40 without a frame (first frame 46). As a result, the first frame 46 only needs to be provided below the oscillating base plate portion 24, so the space between the outer periphery of the oscillating scroll 22 and the inner wall surface of the body vessel 42 is wider than when the first frame 46 has an outer wall. Therefore, compared to when an outer wall is provided, there is no restriction on the size of the oscillating scroll 22, and the outer diameter of the oscillating base plate portion 24 and the winding diameter of the oscillating spiral teeth 26 can be increased. In addition, since the spiral can be increased, it is effective in ensuring performance with low GWP refrigerants (low density refrigerants).

Embodiment 2.
Fig. 10 is a partial cross-sectional view showing a schematic configuration of a compressor according to embodiment 2. Fig. 11 is a cross-sectional view showing a schematic positional relationship between the orbiting scroll 22 and the first frame 46 when the orbiting scroll 22 is shifted to the right in the compressor 100 according to embodiment 2. Fig. 12 is a vertical cross-sectional view showing a schematic positional relationship between the orbiting scroll 22, the first frame 46, and the rotating shaft 33 when the orbiting scroll 22 is shifted to the left in the compressor 100 of Fig. 11.

As shown in Figure 10, embodiment 2 differs from embodiment 1 in that the structure that limits the diameter of the oscillating bed portion 24 or the size of the range of motion R1 (see Figure 11) of the oscillating bed portion 24 is a recess provided in the first frame 46. In the example shown in Figure 11, suction ports 46a are provided on both circumferential sides of the recess in the first frame 46, and the recess and the two suction ports 46a are structures that limit the diameter, etc., of the oscillating bed portion 24. In embodiment 2, the same parts as in embodiment 1 are given the same reference numerals, and the differences from embodiment 1 will be mainly described.

In the second embodiment, as shown in FIG. 10, a recess 46a1 used for adjusting the assembly phase with the fixed base plate portion 23 of the fixed scroll 21 is formed on the upper surface of the outer periphery of the first frame 46. In the example shown in FIG. 11, the recess 46a1 of the first frame 46 has a circular shape when viewed from the axial direction and is provided on the left side of the first frame 46, that is, between the two suction ports 46a. Also, as shown in FIG. 10, a hole 23a is formed on the lower surface of the fixed base plate portion 23 at a position facing the recess 46a1 of the first frame 46 when viewed from the axial direction. The hole 23a of the fixed base plate portion 23 has the same shape as the recess 46a1 of the first frame 46 when viewed from the axial direction.

The hole 23a of the fixed base plate portion 23 may be a through hole as shown in FIG. 10, or may be a recess in which the lower surface of the fixed base plate portion 23 is recessed upward. A protrusion extending downward may be provided on the lower surface of the fixed base plate portion 23 at a position facing the recess 46a1 of the first frame 46 when viewed from the axial direction, and the hole 23a may be provided on the lower surface of this protrusion. The positions at which the recess 46a1 and the suction port 46a are provided in the first frame 46 are not limited to the above positions. However, it is preferable that these multiple structures are concentrated in one area of the outer periphery of the first frame 46 (for example, the left half).

During the manufacturing stage of the compressor 100, the phase is set by the phase setting member 6 so that the first frame 46 and the fixed base plate portion 23 face each other in a predetermined phase in the body container 42. The phase setting member 6 is, for example, a cylindrical pin. When the assembly phase is set, the upper end of the phase setting member 6 is inserted into the hole 23a of the fixed base plate portion 23, and the lower end of the phase setting member 6 is inserted into the recess 46a1 of the first frame 46. After the assembly phase is set, the phase setting member 6 is removed. Note that the phase setting member 6 may not be removed after assembly. When the phase setting member 6 is removed, a sealing member (not shown) that suppresses the flow of refrigerant through the hole 23a of the fixed base plate portion 23 may be provided in the hole 23a. The sealing member may be formed by removing the phase setting member 6 from the recess 46a1 and retaining it inside the hole 23a.

12, in the second embodiment, as in the first embodiment, the position of the center line 54 of the oscillating base plate portion 24 is eccentric from the position of the center line 53 of the boss portion 27 when viewed from the axial direction. Therefore, as shown in FIG. 11, the center line 51 of the movable range R1 of the oscillating base plate portion 24 is eccentric from the center line 52 of the first frame 46.

11, when viewed from the axial direction, the recess 46a1 of the first frame 46 is provided in the non-movable range R2 of the oscillating base plate portion 24. Therefore, as shown in FIG. 12, even when the oscillating base plate portion 24 is closest to the recess 46a1 while the compressor 100 is in operation, the recess 46a1 of the first frame 46 is not covered by the oscillating base plate portion 24.

As described above, in the compressor 100 according to the second embodiment, as in the first embodiment, the center line 54 of the oscillating base plate portion 24 of the oscillating scroll 22 differs from the center line 53 of the boss portion 27 when viewed from the axial direction. Therefore, in the present disclosure, the maximum width Wmax (see FIG. 4) of the non-movable range R2 of the oscillating base plate portion 24 is larger than in the past, and there is room to enlarge the oscillating base plate portion 24 or to enlarge structural parts such as the recess 46a1. As a result, the compressor 100 according to the second embodiment also has the same effect as the first embodiment.

In the compressor 100 of the second embodiment, a recess 46a1 is formed in the non-movable range R2, which is on the outer periphery of the movable range R1 of the oscillating bed section 24, on the opposing surface of the frame (first frame 46) that faces the second surface (lower surface) of the oscillating bed section 24 when viewed from the axial direction. Thus, by providing the recess 46a1 in the non-movable range R2, it becomes easy to position the first frame 46 in the intended phase within the pressure vessel 40.

In addition, in the example shown in Figure 11, by dividing the suction port 46a into two locations, it is possible to leave some shrink-fitting areas, and therefore it is possible to ensure a place for shrink-fitting and fixing the fixed spiral, and to ensure the shrink-fit holding force, compared to the case in which the suction port 46a is provided over a wide area in one location as in embodiment 1.

In addition, in embodiment 2, the fixed spiral teeth 25 and the oscillating spiral teeth 26 may also be arranged as in the first to third modified examples of embodiment 1.

Embodiment 3.
Fig. 13 is a cross-sectional view showing a schematic positional relationship between the orbiting scroll 22 and the first frame 46 when the orbiting scroll 22 is shifted to the right in the compressor 100 according to the third embodiment. Fig. 14 is a vertical cross-sectional view showing a schematic positional relationship between the orbiting scroll 22, the first frame 46, and the rotating shaft 33 when the orbiting scroll 22 is shifted to the left in the compressor 100 shown in Fig. 13. The outline arrows shown in Fig. 13 and Fig. 14 indicate the direction of the refrigerant.

13 and 14, the third embodiment differs from the first embodiment in that the structure that limits the diameter of the oscillating platen portion 24 or the size of the range of motion R1 of the oscillating platen portion 24 is a protrusion provided on the first frame 46. In the third embodiment, the same parts as in the first embodiment are given the same reference numerals, and the differences from the first embodiment will be mainly described.

14, in the third embodiment, the suction port 46a (see FIG. 5) of the first embodiment is not provided in the oscillating base plate portion 24, and the suction pipe 44 is installed between the first frame 46 and the fixed scroll 21 in the height direction (arrow Z direction) of the body container 42. In other words, in the third embodiment, the refrigerant from the suction pipe 44 is directly supplied to the refrigerant suction space Si without passing through the motor space Sm. In addition, in the third embodiment, the discharge pipe 45 is installed in the motor space Sm below the first frame 46 in the height direction (arrow Z direction) of the body container 42. In other words, in the third embodiment, the space above the fixed scroll 21 in the space inside the pressure vessel 40 is a high-pressure space without an opening, and the motor space Sm below the first frame 46 doubles as a discharge space.

As shown in Fig. 13, in the third embodiment, a portion of the outer periphery of the first frame 46 is cut out in the circumferential direction. Then, as shown in Fig. 14, a partition wall 46a2 extending upward toward the fixed base plate portion 23 (see Fig. 1) is provided at the edge of the cutout portion 46c in the first frame 46. As shown in Fig. 13, when viewed from the axial direction, both side ends of the partition wall 46a2 are connected to the inner wall surface of the body container 42, and a communication passage 7 is formed so as to be surrounded by the partition wall 46a2 and the inner wall surface of the body container 42. As shown in Fig. 14, the communication passage 7 communicates between the upper high pressure space (not shown) and the lower motor space Sm.

Although not shown, an opening is formed in the fixed base plate portion 23 (see FIG. 1) at a position facing the cutout portion 46c of the first frame 46 in the axial direction, and this opening serves as a refrigerant inlet of the communication passage 7, and the cutout portion 46c of the first frame 46 serves as a refrigerant outlet of the communication passage 7. The high-pressure refrigerant discharged from the compression mechanism portion 10 and filling the high-pressure space moves through the communication passage 7 to the motor space Sm and is discharged to the outside (e.g., a condenser) via the discharge pipe 45.

As shown in Figure 14, in the third embodiment, as in the first embodiment, the position of the center line 54 of the oscillating base plate portion 24 is eccentric from the position of the center line 53 of the boss portion 27 when viewed from the axial direction. Therefore, as shown in Figure 13, the center line 51 of the range of motion R1 of the oscillating base plate portion 24 is eccentric from the center line 52 of the first frame 46.

13, when viewed from the axial direction, the isolation wall 46a2 of the first frame 46 is provided in the non-movable range R2 of the oscillating base plate portion 24. Therefore, as shown in FIG. 14, even when the oscillating base plate portion 24 is closest to the isolation wall 46a2 while the compressor 100 is in operation, the oscillating base plate portion 24 does not interfere with the isolation wall 46a2.

As described above, in the compressor 100 according to the third embodiment, as in the first embodiment, the center line 54 of the oscillating base plate portion 24 of the oscillating scroll 22 is different from the center line 53 of the boss portion 27. Therefore, in the present disclosure, the maximum width Wmax of the non-movable range R2 of the oscillating base plate portion 24 is larger than in the past, and there is room to enlarge the oscillating base plate portion 24 or to enlarge the communication path 7. As a result, the compressor 100 according to the third embodiment also has the same effect as the first embodiment.

In addition, in the compressor 100 of embodiment 3, a convex portion (isolation wall 46a2) is formed on the opposing surface of the frame (first frame 46) that faces the second surface (lower surface) of the oscillating base plate portion 24, in the non-movable range R2 that is outer circumferentially further than the movable range R1 of the oscillating base plate portion 24 when viewed from the axial direction.

When the communication passage 7 is provided, the communication passage 7 and the refrigerant suction space Si are isolated by the isolation wall 46a2, ensuring airtightness. As a result, loss of power input caused by leakage of the high-pressure refrigerant filling the communication passage 7 into the refrigerant suction space Si is suppressed, and performance can be improved.

In addition, in the third embodiment, the fixed spiral teeth 25 and the oscillating spiral teeth 26 may be arranged as in the first to third modified examples of the first embodiment. However, in the third embodiment, the arrangement of the compression chamber inlet 11a may be determined according to its positional relationship with the intake pipe 44. In FIG. 13, the intake pipe 44 is provided on the right side, so the compression chamber inlet 11a is arranged in the same manner as in FIG. 7, or on the opposite side to that in FIG. 9. In addition, if the intake pipe 44 is provided at the bottom, the phases of the fixed spiral teeth 25 and the oscillating spiral teeth 26 are also rotated accordingly.

It is possible to combine the various embodiments, modify the various embodiments, or omit the various embodiments as appropriate. For example, in the first embodiment, as in the second embodiment, the suction port 46a may be provided in two separate locations.

3 discharge port, 4 chamber, 4a concave portion, 4b chamber discharge port, 5 discharge valve mechanism, 5a discharge valve, 5b valve holder, 5c fixed member, 6 phase determining member, 7 communication passage, 10 compression mechanism portion, 11 compression chamber, 11a compression chamber inlet, 20 discharge valve mechanism, 21 fixed scroll, 22 swing scroll, 23 fixed base plate portion, 23a hole, 24 swing base plate portion, 24a first Oldham groove, 25 fixed spiral tooth, 25e end of winding portion, 26 swing spiral tooth, 26e end of winding portion, 27 boss portion, 28 bush, 28a slider, 28b balance weight, 28b1 weight portion, 29 Oldham ring, 29b upper surface protrusion, 29r ring portion, 30 motor portion, 31 stator, 32 rotor, 33 Rotating shaft, 33a eccentric shaft portion, 33b main shaft portion, 33c oil passage, 40 pressure vessel, 41 upper vessel, 42 body vessel, 43 lower vessel, 44 suction pipe, 45 discharge pipe, 46 first frame, 46a suction port, 46a1 recess, 46a2 isolation wall, 46b bearing portion, 46c notch portion, 46f boss accommodating portion, 46o Oldham accommodating portion, 46o1 second Oldham groove, 46s thrust plate, 47 second frame, 48 ball bearing, 50 boundary, 51 center line, 52 center line, 53 center line, 54 center line, 100 compressor, Ax1 center line, Ax2 center line, R1 movable range, R2 non-moving range, Si refrigerant suction space, Sm motor space, So discharge space, Lp Center position, Wmax maximum width.

Claims (9)

a compression mechanism portion having a fixed scroll and an orbiting scroll and compressing a refrigerant;
A rotating shaft having an eccentric portion;
an electric motor unit that drives the compression mechanism unit via the rotating shaft;
a pressure vessel in which the compression mechanism and the electric motor are housed;
a frame fixed inside the pressure vessel and supporting the orbiting scroll in an axial direction along which the rotation shaft extends;
The orbiting scroll is
A swing base plate portion;
an orbiting spiral tooth provided on a first surface of the orbiting base plate portion on the fixed scroll side;
a boss portion provided on a second surface of the oscillating base plate portion, the second surface being a reverse surface of the first surface, into which the eccentric portion is fitted;
When viewed from the axial direction, the oscillating plate portion and the boss portion are provided such that the position of the center of the oscillating plate portion is different from the position of the center of the boss portion so that the center of the movable range of the oscillating plate portion is eccentric from the center of the frame . The scroll compressor according to claim 1 , wherein a suction port for supplying refrigerant to the compression mechanism is formed in a non-moving area of the frame that is on the outer circumferential side of the movable area of the oscillating base plate when viewed in the axial direction. The scroll compressor according to claim 1 , wherein a recess is formed in a non-movable area of the oscillating base plate portion that is located on an outer circumferential side of the movable area of the oscillating base plate portion when viewed in the axial direction, on an opposing surface of the frame that faces the second surface of the oscillating base plate portion. The scroll compressor according to claim 1 , wherein a convex portion is formed on an opposing surface of the frame that faces the second surface of the oscillating base plate portion, in a non-movable area that is on the outer circumferential side of the movable area of the oscillating base plate portion when viewed in the axial direction. The scroll compressor according to claim 2 , wherein the suction port is formed on a side of the frame opposite to an eccentric direction of a center of a movable range of the oscillating base plate portion when viewed in the axial direction. The fixed scroll has a fixed base plate portion and a fixed spiral tooth provided on a surface of the fixed base plate portion facing the orbiting scroll,
6. The scroll compressor according to claim 2, wherein two compression chamber inlets formed by the oscillating scroll teeth and the fixed scroll teeth are provided so as to have equal linear distances from the suction port when viewed in the axial direction. The fixed scroll has a fixed base plate portion and a fixed spiral tooth provided on a surface of the fixed base plate portion facing the orbiting scroll,
6. The scroll compressor according to claim 2 or 5, wherein, as viewed in the axial direction, one of the two compression chamber inlets formed by the oscillating scroll teeth and the fixed scroll teeth faces the suction port and the other faces the side opposite the suction port, and a linear distance between the other inlet and the suction port is closer than a linear distance between the one inlet and the suction port. The fixed scroll has a fixed base plate portion and a fixed spiral tooth provided on a surface of the fixed base plate portion facing the orbiting scroll,
the oscillating spiral tooth and the fixed spiral tooth are longer than the other so that winding ends are disposed at the same position in the circumferential direction;
The scroll compressor according to claim 2 or 5, wherein a compression chamber inlet formed by the oscillating scroll teeth and the fixed scroll teeth is provided on the radial side of the suction port. The scroll compressor according to any one of claims 1 to 8, wherein the fixed scroll is fixed directly to the pressure vessel without using the frame.

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