WO2019207784A1

WO2019207784A1 - Scroll compressor and refrigeration cycle device

Info

Publication number: WO2019207784A1
Application number: PCT/JP2018/017261
Authority: WO
Inventors: 浩平達脇; 修平小山; 石園　文彦
Original assignee: 三菱電機株式会社
Priority date: 2018-04-27
Filing date: 2018-04-27
Publication date: 2019-10-31
Also published as: JPWO2019207784A1; JP6903228B2; CN112041561A

Abstract

This scroll compressor is provided with a stationary scroll, an orbiting scroll, and a thrust plate. An oil holding space is formed on the inside of the thrust plate, a compression chamber is formed between the stationary scroll and the orbiting scroll, the orbiting scroll is provided with an oil supply groove, and the thrust plate has an oil supply hole. The oil supply groove is provided with: an oil inflow section into which lubricating oil flows; an oil flow section, one side of which is in communication with the oil inflow section, and which extends in the rotational direction of the orbiting scroll from the oil inflow section; and an oil outflow section which is in communication with the other side of the oil inflow section and which, when positioned over the oil supply hole, allows the lubricating oil having flowed through the oil flow section to flow out to the oil supply hole side. One orbital rotation of the orbiting scroll includes: a first period of rotation, in which the oil flow section is positioned over the thrust plate, and the lubricating oil is supplied to the oil supply hole through the oil flow section; and a second period of rotation, in which the oil flow section is positioned over the oil holding space, and the amount of the lubricating oil supplied to the oil supply hole through the oil flow section is less than that in the first period of rotation.

Description

Scroll compressor and refrigeration cycle apparatus

The present invention relates to a scroll compressor and a refrigeration cycle apparatus in which an oil supply hole is provided in a thrust plate.

In the conventional scroll compressor, the swing scroll and the fixed scroll each have a substantially symmetrical spiral body, and the swing scroll and the fixed scroll are housed in a frame having a refrigerant inlet for sucking refrigerant. ing. The swinging scroll in the frame performs a swinging motion, whereby the refrigerant sucked from the refrigerant suction port is compressed. At this time, the oscillating scroll oscillates while sliding on the thrust bearing surface. In order to improve the slidability of the oscillating scroll, a thrust plate is disposed between the oscillating scroll and the frame. Has been.

In such a scroll compressor, in order to reduce the sliding resistance of each sliding part, lubricating oil flows through each sliding part (for example, refer to Patent Document 1). In Patent Document 1, the thrust bearing surface of an orbiting scroll is used for the purpose of improving the slidability between the scrolls of the orbiting scroll and the fixed scroll and reducing the leakage loss of refrigerant by improving the sealing performance during low-speed rotation. An oil supply hole is provided, and the thrust plate is provided with an oil supply hole, and a scroll compressor that secures the required amount of oil supplied to the spiral by intermittently supplying oil from the oil supply hole to the oil supply hole. It is disclosed.

JP 2013-133715 A

If the configuration of Patent Document 1 is adopted, a required amount of oil can be secured when the scroll compressor rotates at a low speed. However, the amount of oil supply during high-speed rotation becomes excessive, leading to a decrease in refrigeration capacity and performance as the amount of oil rises.

The present invention is for solving the above-mentioned problems, while ensuring the required amount of oil supply at low speed rotation, while preventing increase in the oil supply amount at high speed rotation, the amount of oil rising can be adjusted, and the refrigerating capacity is improved. It is another object of the present invention to provide a scroll compressor and a refrigeration cycle device that improve performance.

A scroll compressor according to the present invention includes a fixed scroll having a fixed-side spiral body, a swing scroll having a swing-side spiral body combined with the fixed-side spiral body of the fixed scroll, and a lower surface of the swing scroll. A working fluid that is supported between the fixed scroll and the orbiting scroll, and has an oil reservoir space formed inside the thrust plate. A scroll compressor having a compression chamber for sucking in, wherein the orbiting scroll is provided on a sliding surface that slides with the thrust plate, and includes an oil supply groove to which lubricating oil is supplied, The thrust plate has an oil supply hole that leads from the surface that slides with the orbiting scroll to the compression chamber, and the oil supply groove has an oil inflow portion into which lubricating oil flows; When the oil flow part is located on the oil supply hole, the other side communicates with the oil inflow part, extends from the oil inflow part in the rotation direction of the rocking scroll, and communicates with the other side of the oil circulation part. An oil outflow part that causes the lubricating oil that has passed through the part to flow out to the oil supply hole side, and the oil circulation part is positioned on the thrust plate in one rotation in which the swing scroll swings, A first rotation period in which lubricating oil is supplied to the oil supply hole via an oil circulation part; and the oil circulation part is located on the oil reservoir space and is supplied to the oil supply hole via the oil circulation part. And a second rotation period in which the amount of lubricating oil is less than the first rotation period.

A refrigeration cycle apparatus according to the present invention includes the scroll compressor described above.

According to the scroll compressor and the refrigeration cycle apparatus according to the present invention, the oil circulation portion extending in the rotation direction of the rocking scroll is formed between the oil inflow portion and the oil outflow portion in the oil supply groove. And lubricating oil can be supplied to an oil supply hole via an oil distribution part in the 1st rotation period. In addition, the amount of lubricating oil supplied to the oil supply hole via the oil circulation part is reduced in the oil circulation part in the second rotation period and connected to the oil reservoir space inside the thrust plate, compared to the first rotation period. Therefore, the higher the rotation speed, the more limited the movement of the lubricating oil in the oil circulation portion that should reach the oil supply hole. For this reason, while ensuring the required amount of oil during low-speed rotation, the increase in oil amount during high-speed rotation can be prevented, the amount of oil rise can be adjusted, and the refrigeration capacity and performance can be improved at any rotational speed. be able to.

It is a longitudinal cross-sectional view which shows the cross-sectional structural example of the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows an example of the thrust plate in the scroll compressor of FIG. It is a top view which shows an example of the thrust bearing surface of the rocking | fluctuating scroll in the scroll compressor of FIG. It is a schematic diagram which shows the positional relationship of the oil supply hole and oil supply groove | channel when a rocking | fluctuation scroll rotates in the scroll compressor of FIG. It is a top view which shows an example of the thrust plate in the scroll compressor which concerns on the modification 1 of this invention. It is a top view which shows an example of the thrust bearing surface in the scroll compressor which concerns on the modification 1 of this invention. It is a vertical schematic sectional drawing of the scroll compressor which concerns on Embodiment 2 of this invention. It is a disassembled perspective view of the main frame of the scroll compressor which concerns on Embodiment 2 of this invention, a rocking scroll, etc. It is an enlarged view of the area | region of the dashed-dotted line of FIG. It is an enlarged view of the area | region of the dashed-two dotted line of FIG. It is the figure which looked at the main frame of FIG. 7 from the top. It is a schematic diagram which shows the positional relationship of the oil supply hole and oil supply groove | channel when a rocking | fluctuation scroll rotates in the scroll compressor of FIG. It is a figure for demonstrating one manufacturing method of the main shell of FIG. It is sectional drawing of the scroll compressor which concerns on the modification 2 of this invention. It is an enlarged view of the area | region of the dashed-two dotted line of FIG. It is a figure for demonstrating one manufacturing method of the main shell which concerns on the modification 2 of this invention. It is sectional drawing of the scroll compressor which concerns on the modification 3 of this invention. It is an enlarged view of the area | region of the dashed-two dotted line of FIG. It is sectional drawing of the scroll compressor which concerns on the modification 4 of this invention. It is sectional drawing of the scroll compressor which concerns on the modification 5 of this invention. It is sectional drawing of the scroll compressor which concerns on the modification 6 of this invention. It is sectional drawing of the scroll compressor which concerns on the modification 7 of this invention. It is a refrigerant circuit figure which shows the refrigerating-cycle apparatus which concerns on Embodiment 3 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in each figure, what attached | subjected the same code | symbol is the same or it corresponds, and this is common in the whole text of a specification. Further, in the drawings of the sectional views, hatching is appropriately omitted in view of visibility. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing a cross-sectional configuration example of a scroll compressor 100 according to Embodiment 1 of the present invention. The scroll compressor 100 includes a shell 1, a fixed scroll 31, a swing scroll 32, a main frame 2, a thrust plate 24, and the like. Further, the scroll compressor 100 includes a drive mechanism unit 4 including a motor and the like housed in the shell 1. The scroll compressor 100 is illustrated as a so-called vertical scroll compressor in which the fixed scroll 31 and the swing scroll 32 are disposed on the upper side in the shell 1 and the drive mechanism unit 4 is disposed on the lower side.

The shell 1 forms a sealed space inside, and includes a main shell 11, an upper shell 12 provided on the upper portion of the main shell 11, and a lower shell 13 provided on the lower portion of the main shell 11. ing. A suction pipe 14 for sucking a working fluid such as a refrigerant gas to be compressed is connected to the main shell 11. A discharge pipe 15 for discharging a working fluid such as a compressed refrigerant gas is connected to the upper shell 12. The inside of the main shell 11 is a low pressure chamber 11a, and the inside of the upper shell 12 is a high pressure chamber 12a. The main frame 2 is fixed to the upper side of the main shell 11, and the subframe 5 holding the main shaft portion 61 is fixed to the lower side. The lower shell 13 is an oil sump for storing lubricating oil.

The fixed scroll 31 includes a first substrate 311 and a first spiral body 312 as a fixed-side spiral body that is a spiral projection provided on one surface of the first substrate 311. The first substrate 311 is fixed to the upper side of the main frame 2 with a bolt or the like, and a discharge hole 351 for discharging a working fluid such as a compressed refrigerant gas or the like is formed in the center of the first substrate 311. ing. A discharge valve 36 is provided on the discharge hole 351 to prevent the refrigerant from flowing backward from the high pressure chamber 12a to the discharge hole 351 side.

The swing scroll 32 includes a second substrate 321 and a second spiral body 322 as a swing side spiral body which is a spiral projection provided on one surface of the second substrate 321. The second substrate 321 is swingably supported in the main frame 2. That is, the other surface of the orbiting scroll 32 acts as a sliding surface 3211 that is a thrust bearing surface that slides on the main frame 2 via the thrust plate 24, and a load generated during operation is transmitted via the sliding surface 3211. Supported in the main frame 2. The second spiral body 322 has substantially the same shape as the first spiral body 312 and is combined with the first spiral body 312 to combine the second spiral body 322 and the first spiral body 312 with each other. It is housed in the main frame 2 in a state. The orbiting scroll 32 has a hollow cylindrical portion 323 at the center of the other surface (sliding surface 3211 side). An eccentric shaft portion 62 provided at the upper end of the main shaft portion 61 is inserted into the cylindrical portion 323. The orbiting scroll 32 performs an orbiting motion as a revolving motion with respect to the fixed scroll 31 when the main shaft portion 61 rotates.

In the state where the fixed scroll 31 and the swing scroll 32 are combined, the winding directions of the first spiral body 312 and the second spiral body 322 are opposite to each other. A compression chamber 34 is formed between the second spiral body 322 and the first spiral body 312. Note that the fixed scroll 31 and the orbiting scroll 32 have front end surfaces of the first spiral body 312 and the second spiral body 322 in order to reduce refrigerant leakage from the front end surfaces of the first spiral body 312 and the second spiral body 322. Are provided with

seals

316 and 325, respectively.

The main frame 2 houses the orbiting scroll 32 and the fixed scroll 31 and is fixed to the upper part of the shell 1. The main frame 2 is provided with a refrigerant suction port through which the refrigerant sucked from the suction pipe 14 flows. The main frame 2 has a main bearing portion 22 that rotatably supports the upper portion of the main shaft portion 61.

The thrust plate 24 is provided between the main frame 2 and the sliding surface 3211 of the orbiting scroll 32. The thrust plate 24 is formed in an annular shape and has an opening at the center so that the cylindrical portion 323 is inserted. (See FIG. 2). This opening is connected to an oil sump space 25 formed below and inside the thrust plate 24. The thrust plate 24 improves the slidability of the sliding surface 3211 when the orbiting scroll 32 revolves around the main frame 2. The orbiting scroll 32 is attached to the main frame 2 via the thrust plate 24. It is in a state of being supported in the axial direction. That is, the thrust plate 24 supports the lower surface of the swing scroll so as to be swingable.

The Oldham ring 33 is disposed between the orbiting scroll 32 and the main frame 2, and transmits the rotational force of the main shaft portion 61 to the orbiting scroll 32 while restricting the rotation of the orbiting scroll 32. . The Oldham ring 33 includes a first key portion 332 as a pair of Oldham keys protruding toward the surface facing the main frame 2 and a second key as a pair of Oldham keys protruding toward the surface facing the orbiting scroll 32. Part 333. Then, the second key portion 333 is fitted on the rocking scroll 32 side, and the first key portion 332 is fitted on the main frame 2 side.

Specifically, the sliding surface 3211 of the orbiting scroll 32 is provided with a second Oldham key groove 324 (see FIG. 3) extending in the radial direction for inserting the second key portion 333. A pair of second Oldham key grooves 324 are provided in line symmetry with respect to a predetermined radius of the orbiting scroll 32. A first Oldham key groove 215 extending in the radial direction for inserting the first key portion 332 is formed on the main frame 2 side. The second Oldham key groove 324 and the first Oldham key groove 215 are formed to extend in the radial direction, for example, at positions shifted in phase by 90 °. Similarly, the 2nd key part 333 and the 1st key part 332 are provided in the position where the phase shifted 90 degrees, for example. The second key portion 333 is fitted in the second Oldham key groove 324 so as to be movable in the radial direction, and the first key portion 332 is fitted in the first Oldham key groove 215 so as to be movable in the radial direction. Then, the second key portion 333 and the first key portion 332 move forward and backward in the second Oldham key groove 324 and the first Oldham key groove 215, respectively, and the rotational force of the drive mechanism portion 4 is controlled while restricting the rotation motion of the orbiting scroll 32. Is transmitted to the orbiting scroll 32 that revolves.

The crankshaft 6 has a main shaft portion 61 and an eccentric shaft portion 62. In the shell 1, the main shaft portion 61 is rotatably supported by a main bearing portion 22 provided in the main frame 2, and a lower portion of the main shaft portion 61 is rotatably supported by a sub bearing portion 51. . The sub-bearing portion 51 is press-fitted and fixed in a bearing housing portion formed at the center portion of the sub-frame 5 provided at the lower portion in the shell 1. An eccentric shaft portion 62 is attached to the upper end of the main shaft portion 61 in an eccentric state with respect to the main shaft portion 61, and the cylindrical portion 323 of the orbiting scroll 32 is provided on the eccentric shaft portion 62 so as to be capable of revolving. .

In addition, the sub-frame 5 is provided with a positive displacement oil pump 52. The oil pump 52 sucks the lubricating oil stored in the lower shell 13 and sends it to each sliding portion via an oil passage 63 formed inside the main shaft portion 61. An oil sump space 25 that is a space communicating with the oil passage 63 is formed between the outer peripheral side of the cylindrical portion 323 of the swing scroll 32 and the main frame 2, and the oil sump space 25 passes through the oil sump space 25. Lubricating oil supplied from the oil passage 63 is supplied. The oil reservoir space 25 communicates with the second Oldham key groove 324 of the swing scroll 32, and the lubricating oil in the oil reservoir space 25 is supplied to the second Oldham key groove 324.

Further, the main shaft portion 61 is provided with a first balance weight 64 and a second balance weight 65 for canceling an imbalance caused by the swing scroll 32 swinging. The first balance weight 64 is fixed to the upper portion of the main shaft portion 61 by shrink fitting, and the second balance weight 65 is fixed to the lower portion of the main shaft portion 61 integrally with the stator 41.

The drive mechanism unit 4 is made of, for example, a motor, and includes a stator 41 fixed to the shell 1 and a rotor 42 fixed to the main shaft unit 61. The stator 41 and the rotor 42 are disposed, for example, below the first balance weight 64. The stator 41 is formed by winding a coil, for example, and is fixed to the main shell 11 by shrink fitting. Electric power is supplied to the stator 41 via a power supply terminal 82 provided on the main shell 11. The rotor 42 has, for example, a permanent magnet and is shrink-fitted and fixed to the main shaft portion 61. Then, when energization of the stator 41 is started, the rotor 42 and the main shaft portion 61 are rotated.

Next, the operation of the scroll compressor 100 will be described with reference to FIG. When power is supplied to the power supply terminal 82 from the outside, a current flows through the coil of the stator 41 and a magnetic field is generated. This magnetic field works to rotate the rotor 42 to generate torque in the rotor 42, and the rotor 42 and the main shaft portion 61 are rotationally driven. When the main shaft portion 61 is rotationally driven, a rotational force is transmitted from the eccentric shaft portion 62 to the orbiting scroll 32, and the orbiting scroll 32 performs a revolving motion while its rotation motion is restricted by the Oldham ring 33. When the rotor 42 rotates, the first balance weight 64 and the second balance weight 65 maintain a balance with respect to the eccentric revolving motion of the orbiting scroll 32.

On the other hand, working fluid such as refrigerant gas flows into the shell 1 through the suction pipe 14. A part of the working fluid such as the refrigerant gas flows into the compression chamber 34 to start the compression process. At this time, the compression chamber 34 moves to the center of the orbiting scroll 32 by the revolving motion of the orbiting scroll 32 to reduce the volume, and the refrigerant gas sucked into the compression chamber 34 is compressed. The compressed refrigerant passes through the discharge hole 38 of the fixed scroll 31, pushes the discharge valve 36 open, and flows into the high pressure chamber 12a. Then, it is discharged from the shell 1 through the discharge pipe 15. The remaining part of the refrigerant gas cools the drive mechanism 4 and the lubricating oil through a notch (not shown) of the steel plate of the stator 41.

At this time, the main frame 2 supporting the sliding surface 3211 receives a load on the sliding surface 3211 generated by the pressure of the refrigerant gas in the compression chamber 34. Further, the centrifugal force generated in the first balance weight 64 and the second balance weight 65 and the load from the working fluid are received by the main bearing portion 22 and the auxiliary bearing portion 51. Further, the low-pressure refrigerant gas in the low-pressure chamber 11a and the high-pressure working fluid in the high-pressure chamber 12a are partitioned by the fixed scroll 31 and the main frame 2, and airtightness is maintained.

Further, when the scroll compressor 100 is operated, the lubricating oil is supplied to the sliding portion where the parts slide. Specifically, the lubricating oil stored in the lower shell 13 flows from the lower part of the main shaft part 61 to the upper side of the main shaft part 61 by the oil pump 52, and from the upper end of the main shaft part 61 to the cylinder of the main shaft part 61 and the orbiting scroll 32. Supplied between the shape portion 323. The lubricating oil flows into the oil sump space 25 in the space on the outer peripheral side of the cylindrical portion 323 while lubricating the sliding portion between the main shaft portion 61 and the cylindrical portion 323 of the orbiting scroll 32. A part of the lubricating oil in the oil reservoir space 25 is supplied to the second Oldham key groove 324. On the other hand, the remaining part of the lubricating oil passes through an oil drain hole (not shown), is discharged to the outside of the main frame 2, and returns to the lower shell 13.

The lubricating oil that has flowed into the compression chamber 34 is mixed with the working fluid in the compression chamber 34. The lubricating oil mixed with the working fluid in the compression chamber 34 adheres to the sliding portions of the first spiral body 312 and the second spiral body 322, improves the airtightness of the compression chamber 34 and suppresses wear.

Thus, the lubricating oil flows into the compression chamber 34 through the thrust plate 24 and the swing scroll 32 in order to lubricate the lubrication portion between the fixed scroll 31 and the swing scroll 32. At this time, if the amount of lubricating oil flowing into the compression chamber 34 is insufficient, a problem due to wear or the like occurs, and if the amount of lubricating oil is excessive, the performance of the scroll compressor 100 is reduced. End up. Therefore, the scroll compressor 100 has a structure for supplying an appropriate amount of lubricating oil to the compression chamber 34.

FIG. 2 is a plan view showing an example of a thrust plate 24 in the scroll compressor of FIG. As shown in FIG. 2, an oil supply hole 24 a is formed in the thrust plate 24 placed on the main frame 2, and the oil supply hole 24 a communicates with the compression chamber 34 (see FIG. 1). The oil supply hole 24 a is formed in the vicinity of the other side opposite to one of a pair of second Oldham key grooves 324 connected to an oil inflow portion 91 described later. Therefore, when the lubricating oil is supplied to the oil supply hole 24a, the lubricating oil is accumulated in the oil supply hole 24a, and thereafter, the lubricating oil is supplied from the oil supply hole 24a to the compression chamber 34. The oil supply hole 24a is provided on the outer peripheral side of the thrust plate 24, and is exposed from the orbiting scroll 32 during a predetermined rotation period when the orbiting scroll 32 revolves. Lubricating oil is supplied to the compression chamber 34 from the oil supply hole 24a during this exposure period. The formation position of the oil supply hole 24a can be appropriately set as necessary.

FIG. 3 is a plan view showing an example of a sliding surface 3211 as a thrust bearing surface in the scroll compressor of FIG. As shown in FIG. 3, an oil supply groove 90 is formed on the sliding surface 3211. The oil supply groove 90 includes an oil inflow portion 91, an oil circulation portion 92, and an oil outflow portion 93. The oil inflow portion 91 is a portion into which the lubricating oil flows, and is connected to, for example, the second Oldham key groove 324 on the swing scroll 32 side. Then, the lubricating oil filled in the second Oldham key groove 324 flows into the oil inflow portion 91. Here, in the 2nd Oldham keyway 324, the 2nd key part 333 reciprocates. For this reason, the space of the second Oldham key groove 324 connected to the oil inflow portion 91 is expanded or narrowed by the reciprocating motion of the second key portion 333. When the space of the second Oldham key groove 324 connected to the oil inflow portion 91 is narrowed, the second key portion 333 exhibits a pump function of pumping the lubricating oil, and the oil inflow portion 91 is filled in the second Oldham key groove 324. The lubricating oil that has been inflowed.

The oil circulation part 92 has one side communicating with the oil inflow part 91 and is formed so as to extend from the oil inflow part 91 toward the rotation direction of the rocking scroll 32 (arrow R direction). Here, the oil circulation portion 92 is formed in, for example, an arc shape, and the arc shape has a shape along the rotation trajectory of the rocking scroll 32. That is, the oil circulation part 92 is formed in an obtuse arc shape along the circumferential direction between the outer periphery and the inner periphery of the orbiting scroll 32. When the oscillating scroll 32 is oscillating, the lubricating oil flowing through the oil circulating portion 92 has a relatively weak reaction force, and the flow of the oscillating motion in the rotational direction (arrow R direction) is suppressed.

The oil outflow portion 93 communicates with the other side of the oil circulation portion 92 and causes the lubricating oil that has passed through the oil circulation portion 92 to flow out into the oil supply hole 24a. The oil outflow part 93 is provided, for example, at the tip of the arc-shaped oil circulation part 92. In other words, the oil outflow portion 93 is provided on the rotational direction (arrow R direction) side of the oil inflow portion 91. When the oil outflow portion 93 is positioned on the oil supply hole 24a formed in the vicinity of the other side opposite to one of the pair of second Oldham key grooves 324 connected to the oil inflow portion 91, the oil circulation portion Lubricating oil flowing through 92 is supplied to the oil supply hole 24a. Here, the oil supply groove 90 is formed so that the oil outflow portion 93 is positioned on the oil supply hole 24a during the first rotation period while the swing scroll 32 performs the swing motion of one rotation. .

FIG. 4 is a schematic diagram showing the positional relationship between the oil supply hole 24a and the oil supply groove 90 when the orbiting scroll 32 rotates in the scroll compressor 100 of FIG. In FIG. 4, a predetermined rotational position of the orbiting scroll 32 is represented by a rotation period θ, and the orbiting scroll 32 during one rotation in which θ is 0 ° to 365 ° is rotated by 45 °. ing. First, in the second rotation period of the rotation period θ = 0 ° to 135 °, the oil outflow portion 93 of the oil supply groove 90 is located on the oil supply hole 24a. However, a part of the oil circulation part 92 swings to the center side and is connected to the oil sump space 25 inside the thrust plate 24, and the amount of lubricating oil supplied to the oil supply hole 24a via the oil circulation part 92 is reduced. Less. For example, during the second rotation period, the lubricating oil is not supplied to the oil supply hole 24 a and the lubricating oil is not supplied to the compression chamber 34. For example, the lubricating oil is returned to the oil sump space 25 during the second rotation period.

During the rotation period θ = 135 ° to 180 °, the oil supply hole 24a is exposed from the outer periphery of the orbiting scroll, and the oil supply hole 24a is connected to the compression chamber 34. Therefore, when the oil supply hole 24a is filled with oil, the oil filled in the oil supply hole 24a is supplied to the compression chamber 34 as lubricating oil.

In the first rotation period of the rotation period θ = 180 ° to 315 °, all of the oil circulation portion 92 is located on the thrust plate 24 and is not connected to the oil sump space 25, and is connected via the second Oldham key groove 324. The lubricating oil that has flowed into the oil inflow portion 91 flows through the oil circulation portion 92. Further, at this time, since the moving direction of the lubricating oil moving through the oil circulation portion 92 is substantially the same as the rotational direction of the orbiting scroll 32, the reaction force is weakened against the movement of the lubricating oil, and relatively to the oil outflow portion 93. The transporting action of the oil flow toward it is suppressed. Then, in the vicinity of the rotation period θ = 315 °, the oil outflow portion 93 of the oil supply groove 90 is positioned again on the oil supply hole 24a, and the oil outflow portion 93 and the oil supply hole 24a are connected to each other through the oil circulation portion 92. When the lubricating oil reaches the outflow portion 93, the lubricating oil is filled from the oil outflow portion 93 into the oil supply hole 24a.

Thus, in the period in which the orbiting scroll 32 rotates once, the first rotation period in which the lubricating oil is supplied to the oil supply hole 24a, and the second in which the lubricating oil is difficult to be supplied from the oil supply groove 90 to the oil supply hole 24a. And a third rotation period in which the lubricating oil is supplied to the compression chamber 34 through the oil supply hole 24a. That is, in one rotation in which the swing scroll 32 swings, all of the oil circulation portion 92 is positioned on the thrust plate 24 and the lubricating oil is supplied to the oil supply hole 24a via the oil circulation portion 92. And at least a portion of the oil circulation portion 92 is located on the oil reservoir space 25 inside the thrust plate 24, and the amount of lubricating oil supplied to the oil supply hole 24a via the oil circulation portion 92 is the first amount. A second rotation period that is less than the rotation period. Therefore, the lubricating oil is intermittently supplied to the oil supply hole 24a within one rotation. Further, in the first rotation period in which the lubricating oil is supplied from the oil supply groove 90 to the oil supply hole 24a, whether or not the lubricating oil flows to the oil outflow portion 93 side and is supplied to the oil supply hole 24a is determined by the orbiting scroll. Depends on the rotational speed of 32.

When the scroll compressor 100 is rotated at a low speed, the time required for the swing scroll 32 to make one rotation is longer than that at the time of a high-speed rotation. Therefore, there is sufficient time for oil to be conveyed to the oil supply hole 24a of the thrust plate 24 through the oil supply groove 90 of the swing scroll 32, and the rotation speed of the swing scroll 32 is slow. For this reason, the effect of obstructing the flow of oil in the oil supply groove 90 (oil circulation portion 92) due to the rotation trajectory of the orbiting scroll 32 is low, and the oil supply hole 24a of the thrust plate 24 is provided via the oil supply groove 90 of the orbiting scroll 32. Oil is supplied.

On the other hand, when the scroll compressor 100 is rotated at a high speed, the time required for the rocking scroll 32 to make one rotation is shorter than that during the low-speed rotation. That is, when θ = 180 ° to 315 ° during high-speed rotation, a flow path from the oil inflow portion 91 to the oil circulation portion 92 is formed on the thrust plate 24, and the lubricating oil flows from the oil circulation portion 92 to the oil outflow portion. Head to 93. However, the lubricating oil in the oil circulation part 92 does not allow sufficient time for the movement to reach the oil outflow part 93 with respect to the rocking scroll 32 during high-speed rotation, and the oil outflow part in the oil circulation part 92 The movement of the lubricating oil up to 93 is limited. When θ = 0 °, the flow path from the oil inflow portion 91 to the oil circulation portion 92 comes inside the inner diameter of the thrust plate 24, and the lubricating oil falls from the oil circulation portion 92 to the oil sump space 25. Therefore, the supply amount of lubricating oil does not increase. Therefore, there is not enough time for oil to be supplied to the oil supply hole 24a of the thrust plate 24 via the oil supply groove 90 of the orbiting scroll 32, and the rotation speed of the scroll is fast. For this reason, the effect of obstructing the flow of oil in the oil supply groove 90 (oil circulation portion 92) due to the rotation trajectory of the orbiting scroll 32 is high, and the oil supply hole of the thrust plate 24 is provided via the oil supply groove 90 of the orbiting scroll 32. The supply of oil to 24a is suppressed.

In this way, the oil supply groove 90 is formed in the oil supply groove 90 so as to extend in the rotation direction of the orbiting scroll 32, so that the required amount of oil at the time of low speed rotation is secured and the amount of oil supply at the time of high speed rotation is increased. Since the amount of oil rising can be adjusted, the refrigerating capacity can be improved and the performance can be improved. That is, when the oil supply hole is provided in the sliding surface 3211 of the orbiting scroll 32 and the oil supply hole is provided in the thrust plate 24 as in the prior art, the slidability is improved when the scroll compressor rotates at a low speed. Refrigerant leakage loss due to improved sealing performance can be reduced. However, conventionally, as the rotational speed increases, the amount of oil supply increases, so the amount of oil supply becomes excessive during high-speed rotation. As a result, the amount of oil rising during high-speed rotation increases, leading to a reduction in refrigeration capacity and performance.

On the other hand, in the scroll compressor 100 described above, the oil supply hole 24a and the oil supply groove 90 are arranged so that their positions overlap in a predetermined rotation period of the rotation period in which the rocking scroll 32 rotates once. Even in the first rotation period in which the positions overlap, an effect is obtained in which the reaction force is weakened so that the rotation trajectory of the orbiting scroll 32 prevents the oil flow in the oil supply groove 90. Therefore, the amount of oil rising can be adjusted without excessively supplying lubricating oil to the compression mechanism unit 3 during high-speed rotation.

Furthermore, when the oil outflow portion 93 of the oil supply groove 90 is formed so as to be positioned on the oil supply hole 24a during the first rotation period when the swing scroll 32 swings, Since the lubricating oil can be supplied from the oil supply groove 90 to the oil supply hole 24a, it is possible to prevent the lubricating oil from being insufficient during low-speed rotation.

Further, as shown in FIG. 3, when the oil circulation portion 92 is formed in an arc shape, particularly along the rotation path of the orbiting scroll 32, the effect of reducing the reaction force acts on the lubricating oil, The movement of the lubricating oil in the circulation part 92 can be more efficiently regulated.

<Modification 1>
FIG. 5 is a plan view showing an example of the thrust plate 24 in the scroll compressor 100 according to the first modification of the present invention, and FIG. 6 is a slide as a thrust bearing surface in the scroll compressor 100 according to the first modification of the present invention. It is a top view which shows an example of the moving surface 3211, The modification 1 of the scroll compressor 100 is demonstrated with reference to FIG.5 and FIG.6. 5 and FIG. 6, parts having the same configuration as in FIG. 2 and FIG.

5 and FIG. 6, two oil supply holes 24a of the thrust plate 24 and two oil supply grooves 90 of the orbiting scroll 32 are provided. The two oil supply holes 24a and the oil supply groove 90 are formed at positions that are rotationally symmetrical, for example. That is, two oil supply holes 24 a of the thrust plate 24 and two oil supply grooves 90 of the orbiting scroll 32 are provided symmetrically with respect to a predetermined radius of the thrust plate 24 and the orbiting scroll 32.

According to the first modification, since the oil supply groove 90 and the two oil supply holes 24a are provided, the amount of oil supplied to the compression chamber 34 can be increased, so that the required amount of oil during low-speed rotation is ensured. Even when it is not possible, the required amount of oil can be secured as required. Even in this case, since the second rotation period exists, as in the first embodiment, it is possible to suppress an increase in the amount of oil rising and a decrease in performance due to excessive supply of lubricating oil during high-speed rotation. it can.

In addition, this invention is not limited to the said embodiment and modification. For example, in Embodiment 1 and Modification 1 described above, the case where the oil supply groove 90 of the orbiting scroll 32 has an arc shape has been described. However, the present invention is not limited to this shape, and the rotation direction (arrow Any one extending in the R direction) may be used. In other words, the oil circulation portion 92 may be, for example, a linear shape or an oval shape as long as the flow of the lubricating oil from the oil inflow portion 91 to the oil outflow portion 93 in the oil supply groove 90 is obstructed by the rotation trajectory of the orbiting scroll 32. Any shape such as a shape or a polygonal shape may be used. Moreover, in the modification 1, although illustrated about the case where the two oil supply grooves 90 and the oil supply hole 24a are provided, you may provide 3 or more multiple.

Further, in FIG. 3, the oil supply groove 90 communicates with the second Oldham key groove 324, and the case where the lubricating oil is supplied to the oil supply groove 90 through the second Oldham key groove 324 is illustrated. As long as a path through which oil is supplied to the oil supply groove 90 is formed, the shape is not limited to this.

Embodiment 2. FIG.
The second embodiment will be described below. FIG. 7 is a schematic vertical sectional view of scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 8 is an exploded perspective view of the main frame 2, the orbiting scroll 32, and the like of the scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 9 is an enlarged view of the region of the alternate long and short dash line in FIG. The scroll compressor 100 in FIG. 7 is a so-called vertical scroll compressor that is used in a state in which the central axis of the crankshaft 6 is substantially perpendicular to the ground.

The scroll compressor 100 includes a shell 1, a main frame 2, a compression mechanism unit 3, a drive mechanism unit 4, a subframe 5, a crankshaft 6, a bush 7, and a power feeding unit 8. . In the following, with the main frame 2 as a reference, the side (upper side) on which the compression mechanism unit 3 is provided is oriented to one end U and the side (lower side) on which the drive mechanism unit 4 is provided to the other end L. explain.

The shell 1 is a cylindrical casing made of a conductive member such as metal and closed at both ends, and includes a main shell 11, an upper shell 12, and a lower shell 13. The main shell 11 has a cylindrical shape, and a suction pipe 14 is connected to the side wall thereof by welding or the like. The suction pipe 14 is a pipe for introducing a refrigerant into the shell 1 and communicates with the main shell 11. The upper shell 12 is a substantially hemispherical first shell, and a part of the side wall thereof is connected to the upper end portion of the main shell 11 by welding or the like, and covers the upper opening of the main shell 11. A discharge pipe 15 is connected to the upper part of the upper shell 12 by welding or the like. The discharge pipe 15 is a pipe for discharging the refrigerant to the outside of the shell 1 and communicates with the internal space of the main shell 11. The lower shell 13 is a second shell having a substantially hemispherical shape, and a part of the side wall thereof is connected to the lower end portion of the main shell 11 by welding or the like through the connection shell 16, and the lower opening of the main shell 11 is opened. Covering. The shell 1 is supported by a fixing base 17 having a plurality of screw holes. A plurality of screw holes are formed in the fixing base 17, and the scroll compressor can be fixed to other members such as a casing of the outdoor unit by screwing screws into these screw holes.

The main frame 2 is a hollow metal frame in which a cavity is formed, and is provided inside the shell 1. The main frame 2 includes a main body portion 21, a main bearing portion 22, and an oil return pipe 23. The main body 21 is fixed to the inner wall surface of the one end U of the main shell 11, and an accommodation space 211 is formed at the center along the longitudinal direction of the shell 1. The accommodation space 211 has a stepped shape in which one end U is open and the space narrows toward the other end L. An annular flat surface 212 is formed on one end U of the main body 21 so as to surround the accommodation space 211. On the flat surface 212, a ring-shaped thrust plate 24 made of a steel plate material such as valve steel is disposed. Therefore, in the present embodiment, the thrust plate 24 functions as a thrust bearing. A suction port 213 is formed at a position that does not overlap the thrust plate 24 on the outer end side of the flat surface 212. The suction port 213 is a space penetrating in the vertical direction of the main body 21, that is, the upper shell 12 side and the lower shell 13 side. The number of suction ports 213 is not limited to one, and a plurality of suction ports may be formed.

An Oldham accommodating portion 214 is formed in a step portion on the other end side L from the flat surface 212 of the main frame 2. A first Oldham key groove 215 is formed in the Oldham accommodating portion 214. The first Oldham key groove 215 is formed so that a part of the outer end side is shaved on the inner end side of the flat surface 212. Therefore, when the main frame 2 is viewed from the one end side U, a part of the first Oldham key groove 215 overlaps the thrust plate 24. The first Oldham keyway 215 is formed so that a pair faces each other. The main bearing portion 22 is continuously formed on the other end side L of the main body portion 21, and a shaft hole 221 is formed therein. The shaft hole 221 penetrates in the vertical direction of the main bearing portion 22, and its one end U communicates with the accommodation space 211. The oil return pipe 23 is a pipe for returning the lubricating oil accumulated in the accommodation space 211 to the oil sump inside the lower shell 13, and is inserted and fixed in an oil drain hole formed through the inside and outside of the main frame 2. .

Lubricating oil is refrigeration oil containing ester synthetic oil, for example. The lubricating oil is stored in the lower part of the shell 1, that is, in the lower shell 13, sucked up by an oil pump 52 described later, passes through an oil passage 63 in the crankshaft 6, and mechanically contacts the compression mechanism unit 3 and the like. Reduces wear between parts to be used, adjusts the temperature of sliding parts, and improves sealing performance. As the lubricating oil, an oil having an appropriate viscosity as well as excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low-temperature fluidity and the like is suitable.

The compression mechanism unit 3 is a compression mechanism that compresses the refrigerant. The compression mechanism unit 3 is a scroll compression mechanism that includes a fixed scroll 31 and a swing scroll 32. The fixed scroll 31 is made of a metal such as cast iron, and includes a first substrate 311 and a first spiral body 312. The first substrate 311 has a disk shape, and a discharge port 313 is formed through the center in the vertical direction. The first substrate 311 is fixed to the main shell 11. The first spiral body 312 protrudes from the surface on the other end side L of the first substrate 311 to form a spiral wall, and its tip protrudes to the other end side L. The orbiting scroll 32 is made of a metal such as aluminum, and includes a second substrate 321, a second spiral body 322, a cylindrical portion 323, and a second Oldham keyway 324. The second substrate 321 is located on the one surface on which the first spiral body 312 is formed, the other surface in which at least a part of the outer peripheral region becomes the sliding surface 3211, and the outermost surface in the radial direction. And a side surface 3212 connecting the other surface, and the sliding surface 3211 is supported (supported) on the main frame 2 so as to be slidable on the thrust plate 24. The second substrate 321 is disposed between the fixed scroll 31 and the main frame 2 and has a gap with respect to the inner peripheral surface of the main shell 11. The second spiral body 322 projects from one surface of the second substrate 321 to form a spiral wall, and its tip projects to one end U. Note that a seal member for suppressing leakage of the refrigerant is provided at the distal end portion of the first spiral body 312 of the fixed scroll 31 and the second spiral body 322 of the swing scroll 32. The cylindrical portion 323 is a cylindrical boss formed to protrude from the approximate center of the other surface of the second substrate 321 to the other end L. On the inner peripheral surface of the cylindrical portion 323, a rocking bearing for rotatably supporting a slider 71 described later, a so-called journal bearing is provided so that its central axis is parallel to the central axis of the crankshaft 6. . The second Oldham key groove 324 is a long round groove formed on the other surface of the second substrate 321. The second Oldham keyway 324 is provided so that a pair faces each other. A line connecting the pair of second Oldham key grooves 324 is provided to be orthogonal to a line connecting the pair of first Oldham key grooves 215.

An Oldham ring 33 is provided in the Oldham accommodating portion 214 of the main frame 2. The Oldham ring 33 includes a ring portion 331, a first key portion 332, and a second key portion 333. The ring part 331 has a ring shape. The first key portion 332 is formed so as to be opposed to the surface on the other end side L of the ring portion 331, and is accommodated in the pair of first Oldham key grooves 215 of the main frame 2. The second key portion 333 is formed so that a pair thereof faces the surface on one end side U of the ring portion 331, and is accommodated in the pair of second Oldham key grooves 324 of the orbiting scroll 32. When the orbiting scroll 32 revolves due to the rotation of the crankshaft 6, the first key portion 332 slides in the first Oldham key groove 215, and the second key portion 333 slides in the second Oldham key groove 324, whereby the Oldham ring 33 is The rocking scroll 32 is prevented from rotating.

The compression chamber 34 is formed by meshing the first spiral body 312 of the fixed scroll 31 and the second spiral body 322 of the swing scroll 32 with each other. Since the volume of the compression chamber 34 decreases in the radial direction from the outside toward the inside, the compression chamber 34 is gradually compressed by taking the refrigerant from the outer end side of the spiral body and moving it to the center side. The compression chamber 34 communicates with the discharge port 313 at the center of the fixed scroll 31. A muffler 35 having a discharge hole 351 is provided on the surface of one end U of the fixed scroll 31, and a discharge valve 36 that opens and closes the discharge hole 351 to prevent the refrigerant from flowing backward is provided.

The refrigerant is composed of, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a hydrocarbon, or a mixture containing them. Halogenated hydrocarbons having a carbon double bond are HFC refrigerants and chlorofluorocarbon low GWP refrigerants having an ozone layer depletion coefficient of zero. Examples of the low GWP refrigerant include HFO refrigerant, and examples thereof include tetrafluoropropene such as HFO1234yf, HFO1234ze, and HFO1243zf whose chemical formula is represented by C3H2F4. Examples of the halogenated hydrocarbon having no carbon double bond include a refrigerant in which R32 (difluoromethane), R41, and the like represented by CH2F2 are mixed. Examples of the hydrocarbon include natural refrigerants such as propane and propylene. Examples of the mixture include a mixed refrigerant obtained by mixing R32, R41, and the like with HFO1234yf, HFO1234ze, HFO1243zf, and the like.

The drive mechanism 4 is provided on the other end L of the main frame 2 inside the shell 1. The drive mechanism unit 4 includes a stator 41 and a rotor 42. The stator 41 is a stator formed by winding a winding around an iron core formed by laminating a plurality of electromagnetic steel plates, for example, via an insulating layer, and is formed in a ring shape. The stator 41 is fixedly supported inside the main shell 11 by shrink fitting or the like. The rotor 42 is a cylindrical rotor having a built-in permanent magnet inside an iron core formed by laminating a plurality of electromagnetic steel plates and having a through-hole penetrating in the vertical direction in the center, and is disposed in the internal space of the stator 41. ing.

The subframe 5 is a metal frame and is provided on the other end side L of the drive mechanism 4 inside the shell 1. The subframe 5 is fixedly supported on the inner peripheral surface of the other end L of the main shell 11 by shrink fitting or welding. The sub frame 5 includes a sub bearing portion 51 and an oil pump 52. The sub bearing portion 51 is a ball bearing provided on the upper side of the center portion of the sub frame 5 and has a hole penetrating in the vertical direction at the center. The oil pump 52 is provided below the central portion of the sub-frame 5 and is disposed so that at least a part of the oil pump 52 is immersed in the lubricating oil stored in the oil reservoir of the shell 1.

The crankshaft 6 is a long metal rod-like member and is provided inside the shell 1. The crankshaft 6 includes a main shaft portion 61, an eccentric shaft portion 62, and an oil passage 63. The main shaft portion 61 is a shaft constituting a main portion of the crankshaft 6, and is arranged so that the central axis thereof coincides with the central axis of the main shell 11. The main shaft portion 61 has a rotor 42 in contact with the outer surface thereof. The eccentric shaft part 62 is provided on one end side U of the main shaft part 61 so that the central axis is eccentric with respect to the central axis of the main shaft part 61. The oil passage 63 is vertically provided through the main shaft portion 61 and the eccentric shaft portion 62. In the crankshaft 6, one end side U of the main shaft portion 61 is inserted into the main bearing portion 22 of the main frame 2, and the other end side L is inserted and fixed to the sub bearing portion 51 of the subframe 5. As a result, the eccentric shaft portion 62 is disposed in the cylinder of the cylindrical portion 323, and the rotor 42 is disposed such that the outer peripheral surface thereof maintains a predetermined gap from the inner peripheral surface of the stator 41. Further, a first balance weight 64 is provided at one end U of the main shaft portion 61, and a second balance weight 65 is provided at the other end L to cancel the unbalance caused by the swinging of the swing scroll 32.

The bush 7 is made of a metal such as iron and is a connecting member that connects the orbiting scroll 32 and the crankshaft 6. The bush 7 is composed of two parts in the present embodiment, and includes a slider 71 and a balancer 72. The slider 71 is a cylindrical member in which a flange is formed, and is fitted into each of the eccentric shaft portion 62 and the cylindrical portion 323. As shown in FIG. 8, the balancer 72 is a donut-shaped member having a weight portion 721 whose shape viewed from one end U is substantially C-shaped, and is rotated to cancel the centrifugal force of the orbiting scroll 32. It is provided eccentric to the center. The balancer 72 is fitted to the flange of the slider 71 by a method such as shrink fitting.

The power supply unit 8 is a power supply member that supplies power to the scroll compressor, and is formed on the outer peripheral surface of the main shell 11 of the shell 1. The power supply unit 8 includes a cover 81, a power supply terminal 82, and a wiring 83. The cover 81 is a cover member having a bottomed opening. The power supply terminal 82 is made of a metal member, and one is provided inside the cover 81 and the other is provided inside the shell 1. One of the wires 83 is connected to the power supply terminal 82 and the other is connected to the stator 41.

Next, the relationship between the shell 1 and the compression mechanism 3 will be described in more detail with reference to FIGS. FIG. 10 is an enlarged view of a region indicated by a two-dot chain line in FIG. 9.

As shown in FIG. 10, the shell 1 includes a first inner wall surface 111, a first projecting portion 112 that projects from the first inner wall surface 111 and positions the fixed scroll 31, and the first projecting portion 112 on the upper shell 12 side. And a first positioning surface 113 that faces the surface. That is, the main shell 11 includes a stepped portion whose inner diameter increases toward the other end side L. The fixed scroll 31 is fixed to the first inner wall surface 111 by shrink fitting or the like while being positioned on the first positioning surface 113. This structure eliminates the need for a wall for fixing the fixed scroll 31 to the main frame 2 as in the prior art. That is, the wall of the main frame 2 is not interposed between the side surface 3212 of the second substrate 321 of the swing scroll 32 and the inner wall surface of the main shell 11, and the side surface 3212 of the second substrate 321 and the inner wall surface of the main shell 11 are Are arranged to face each other. Therefore, the refrigerant intake space 37 provided between the first substrate 311 of the fixed scroll 31 and the thrust bearing of the main frame 2 in the main shell 11 and in which the orbiting scroll 32 is disposed can be expanded as compared with the conventional case. . Further, since the structure of the main frame 2 is simplified, the workability is improved and the weight can be reduced.

Various advantages can be obtained by expanding the refrigerant intake space 37. For example, in the so-called low pressure shell structure in which the pressure in the space in the main shell 11 in which the drive mechanism unit 4 is disposed and the pressure in the refrigerant intake space 37 is lower than the pressure in the refrigerant intake space 37 as in the present embodiment. Since the second substrate 321 of the orbiting scroll 32 is pressed against the thrust plate 24 by the compressed refrigerant pressure, a thrust load is generated at the sliding portion. Thus, the thrust load can be reduced by increasing the diameter of the second substrate 321 and the thrust plate 24 of the orbiting scroll 32 and increasing the sliding area while maintaining the conventional design of the spiral body. It becomes possible. Therefore, it is a refrigeration cycle apparatus that includes the scroll compressor, the condenser, the expansion valve, and the evaporator according to the present embodiment and circulates the refrigerant, and includes a high-pressure refrigerant that increases the burden on the thrust bearing because it includes R32. Even when used, the reliability can be improved.

Further, as shown in FIG. 9, by making the outer diameter of the upper shell 12 smaller than the one end side of the main shell 11, the fixed scroll 31 is moved between the upper shell 12 and the first positioning surface 113 of the first projecting portion 112. It is comprised so that it may pinch | interpose. Thereby, the fixed scroll 31 can be pressed against the first positioning surface 113 by the upper shell 12 at the time of manufacture, and the positioning accuracy of the fixed scroll 31 can be increased. Further, it is possible to suppress the vertical displacement of the fixed scroll 31 due to vibrations or the like that may occur during transportation or driving of the scroll compressor. When at least a part of the outer wall surface of the upper shell 12 is in contact with the inner wall surface of the main shell 11, the fixing strength due to welding of the main shell 11 and the upper shell 12 is increased, and the fixed scroll 31 is moved in the vertical direction. This is more desirable because it can suppress misalignment.

The main frame 2 is also fixed to the second inner wall surface 114 by shrinkage fitting or the like in a state where the main frame 2 is positioned by the second positioning surface 116 of the second projecting portion 115 projecting from the second inner wall surface 114 of the shell 1. .

FIG. 11 is a view of the main frame 2 as viewed from above. A ring-shaped protruding wall 216 that protrudes toward the upper shell 12 is formed at the outer end of the flat surface 212 of the main frame 2. The thrust plate 24 is arranged on the flat surface 212 inside the protruding wall 216 so as to cover a part of the first Oldham key groove 215. As shown in FIG. 9, the height h of the protruding wall 216 from the flat surface 212 is set to be smaller than the thickness d of the thrust plate 24, so that the orbiting scroll 32 can slide with the thrust plate 24. . In addition, by adjusting the thickness d of the thrust plate 24, it is also possible to set the spiral tip gap, which is the distance between the substrate of one scroll and the spiral body of the other scroll, within a suitable range. For example, the thickness d of the thrust plate 24 is usually about 0.5 mm, but if a thickness d of about 0.6 mm is used, the spiral tip gap can be reduced, and the coolant can flow between the spiral tip and the substrate. Leakage into the adjacent compression space through the gap can be suppressed.

Here, convex portions or concave portions are formed on the thrust plate 24 and the projecting wall 216, and the convex portions and the concave portions are engaged so that rotation of the thrust plate 24 can be suppressed. This is because the flat surface 212 and the thrust plate 24 of the main frame 2 are both ring-shaped, and the thrust plate 24 may rotate with respect to the flat surface 212 as the swing scroll 32 swings. The rotation is suppressed by engaging the convex portion with the concave portion. In the present embodiment, the convex portion includes a pair of protrusions 217 formed to protrude from the protrusion wall 216 in the direction of the thrust plate 24, and the concave portion includes a notch 241 formed on the outer peripheral portion of the thrust plate 24. The pair of protrusions 217 are provided so as to be engaged with opposite sides of the notch 241. A suction port 213 is disposed in a portion located between the pair of protrusions 217 of the main frame 2. That is, since the suction port 213 is arranged in the notch 241 portion, the refrigerant can be taken into the refrigerant take-in space 37 without being blocked by the thrust plate 24.

Next, the operation of the scroll compressor 100 will be described. When the power supply terminal 82 of the power supply unit 8 is energized, torque is generated in the stator 41 and the rotor 42, and the crankshaft 6 rotates accordingly. The rotation of the crankshaft 6 is transmitted to the orbiting scroll 32 via the eccentric shaft portion 62 and the bush 7. The orbiting scroll 32 to which the rotational driving force has been transmitted is restricted from rotating by the Oldham ring 33, and performs an eccentric revolving motion with respect to the fixed scroll 31. At this time, the other surface of the orbiting scroll 32 slides with the thrust plate 24.

As the swinging scroll 32 swings, the refrigerant sucked into the shell 1 from the suction pipe 14 reaches the refrigerant intake space 37 through the suction port 213 of the main frame 2 and swings with the fixed scroll 31. It is taken into a compression chamber 34 formed by the moving scroll 32. Then, the refrigerant is compressed by reducing the volume while moving from the outer peripheral portion toward the center along with the eccentric revolving motion of the orbiting scroll 32. During the eccentric revolving operation of the orbiting scroll 32, the orbiting scroll 32 moves in the radial direction together with the bush 7 by its centrifugal force, and the side walls of the second spiral body 322 and the first spiral body 312 are in close contact with each other. The compressed refrigerant reaches the discharge hole 351 of the fixed scroll 31 from the discharge port 313 of the fixed scroll 31, and is discharged outside the shell 1 against the discharge valve 36.

At this time, the main frame 2 supporting the sliding surface 3211 receives a load on the sliding surface 3211 generated by the pressure of the refrigerant in the compression chamber 34. Further, the centrifugal force generated in the first balance weight 64 and the second balance weight 65 and the load from the working fluid are received by the main bearing portion 22 and the auxiliary bearing portion 51. Further, the low-pressure refrigerant gas in the low-pressure chamber 11a and the high-pressure refrigerant in the high-pressure chamber 12a are partitioned by the fixed scroll 31 and the main frame 2, and airtightness is maintained.

The lubricating oil flowing into the compression chamber 34 is mixed with the refrigerant in the compression chamber 34. The lubricating oil mixed with the refrigerant in the compression chamber 34 adheres to the sliding portions of the first spiral body 312 and the second spiral body 322 to improve the airtightness of the compression chamber 34 and suppress wear.

As shown in FIG. 11, an oil supply hole 24a is formed in the thrust plate 24 placed on the main frame 2, and the oil supply hole 24a communicates with the compression chamber 34 (see FIG. 7). The oil supply hole 24 a is formed in the vicinity of the other side opposite to one of a pair of second Oldham key grooves 324 connected to an oil inflow portion 91 described later. Therefore, when the lubricating oil is supplied to the oil supply hole 24a, the lubricating oil is accumulated in the oil supply hole 24a, and thereafter, the lubricating oil is supplied from the oil supply hole 24a to the compression chamber 34. The oil supply hole 24a is provided between the inner periphery and the outer periphery of the thrust plate 24, and is exposed from the orbiting scroll 32 during a predetermined rotation period when the orbiting scroll 32 revolves. Lubricating oil is supplied to the compression chamber 34 from the oil supply hole 24a during this exposure period. The formation position of the oil supply hole 24a can be appropriately set as necessary.

As shown in FIG. 3 in the first embodiment, an oil supply groove 90 is formed on the sliding surface 3211. The oil supply groove 90 includes an oil inflow portion 91, an oil circulation portion 92, and an oil outflow portion 93. The oil inflow portion 91 is a portion into which the lubricating oil flows, and is connected to, for example, the second Oldham key groove 324 on the swing scroll 32 side. Then, the lubricating oil filled in the second Oldham key groove 324 flows into the oil inflow portion 91. Here, in the 2nd Oldham keyway 324, the 2nd key part 333 reciprocates. For this reason, the space of the second Oldham key groove 324 connected to the oil inflow portion 91 is expanded or narrowed by the reciprocating motion of the second key portion 333. When the space of the second Oldham key groove 324 connected to the oil inflow portion 91 is narrowed, the second key portion 333 exhibits a pump function of pumping the lubricating oil, and the oil inflow portion 91 is filled in the second Oldham key groove 324. The lubricating oil that has been inflowed.

The oil outflow portion 93 communicates with the other side of the oil circulation portion 92 and causes the lubricating oil that has passed through the oil circulation portion 92 to flow out into the oil supply hole 24a. The oil outflow part 93 is provided, for example, at the tip of the arc-shaped oil circulation part 92. In other words, the oil outflow portion 93 is provided on the rotational direction (arrow R direction) side of the oil inflow portion 91. When the oil outflow portion 93 is positioned on the oil supply hole 24a formed in the vicinity of the other side opposite to one of the pair of second Oldham key grooves 324 connected to the oil inflow portion 91, the oil circulation portion Lubricating oil flowing through 92 is supplied to the oil supply hole 24a. Here, the oil supply groove 90 is formed so that the oil outflow portion 93 is positioned on the oil supply hole 24a during the first rotation period while the swing scroll 32 performs the swing motion of one rotation.

FIG. 12 is a schematic diagram showing the positional relationship between the oil supply hole 24a and the oil supply groove 90 when the orbiting scroll 32 rotates in the scroll compressor 100 of FIG. In FIG. 12, the predetermined rotation position of the orbiting scroll 32 is represented by a rotation period θ, and the orbiting scroll 32 during one rotation in which θ is 0 ° to 365 ° is rotated by 45 °. ing. First, in the second rotation period of the rotation period θ = 0 ° to 135 °, the oil outflow portion 93 of the oil supply groove 90 is located on the oil supply hole 24a. However, a part of the oil circulation part 92 swings to the center side and is connected to the oil sump space 25 inside the thrust plate 24, and the amount of lubricating oil supplied to the oil supply hole 24a via the oil circulation part 92 is reduced. Less. For example, during the second rotation period, the lubricating oil is not supplied to the oil supply hole 24 a and the lubricating oil is not supplied to the compression chamber 34. For example, the lubricating oil is returned to the oil sump space 25 during the second rotation period.

Thus, in the period in which the orbiting scroll 32 rotates once, the first rotation period in which the lubricating oil is supplied to the oil supply hole 24a, and the second in which the lubricating oil is difficult to be supplied from the oil supply groove 90 to the oil supply hole 24a. And a third rotation period in which the lubricating oil is supplied to the compression chamber 34 through the oil supply hole 24a. Therefore, the lubricating oil is intermittently supplied to the oil supply hole 24a within one rotation. Further, in the first rotation period in which the lubricating oil is supplied from the oil supply groove 90 to the oil supply hole 24a, whether or not the lubricating oil flows to the oil outflow portion 93 side and is supplied to the oil supply hole 24a is determined by the orbiting scroll. Depends on the rotational speed of 32.

In this way, the oil supply groove 90 is formed in the oil supply groove 90 so as to extend in the rotation direction of the orbiting scroll 32, so that the required amount of oil at the time of low speed rotation is secured and the amount of oil supply at the time of high speed rotation is increased. Since the amount of oil rising can be adjusted, the refrigerating capacity can be improved and the performance can be improved. Here, in the second embodiment, the fixed scroll 31 is fixed to the shell 1. Thereby, the rocking scroll 32 can be enlarged. The swinging scroll 32 that has been increased in size has a problem of the stability of the swinging operation. The swinging operation of the swing scroll 32 is related to the amount of lubricating oil supplied to the swing of the swing scroll 32. Therefore, by adopting a configuration that can prevent the increase in the amount of oil supply at high speed rotation and adjust the amount of oil rise while securing the required oil amount at low speed rotation of the present invention, from low speed rotation to high speed rotation The amount of oil rising can be optimized, and the swing operation of the swing scroll 32 can be stabilized. That is, when the oil supply hole is provided in the sliding surface 3211 of the orbiting scroll 32 and the oil supply hole is provided in the thrust plate 24 as in the prior art, the slidability is improved when the scroll compressor rotates at a low speed. Refrigerant leakage loss due to improved sealing performance can be reduced. However, conventionally, as the rotational speed increases, the amount of oil supply increases, so the amount of oil supply becomes excessive during high-speed rotation. As a result, the amount of oil rising during high-speed rotation increases, leading to a reduction in refrigeration capacity and performance.

On the other hand, in the scroll compressor 100 described above, the oil supply hole 24a and the oil supply groove 90 are arranged so that their positions overlap in a predetermined rotation period of the rotation period in which the orbiting scroll 32 rotates once. Even during the first rotation period, the effect of weakening the reaction force is exhibited so that the rotation trajectory of the orbiting scroll 32 prevents the flow of oil in the oil supply groove 90. Therefore, the lubricating oil is not excessively supplied to the compression mechanism unit 3 at the time of high speed rotation, and the amount of oil rising can be appropriately adjusted even if the swing scroll 32 is enlarged.

Furthermore, when the oil outflow portion 93 of the oil supply groove 90 is formed so as to be positioned on the oil supply hole 24a during the first rotation period when the swing scroll 32 swings, Since the lubricating oil can be supplied from the oil supply groove 90 to the oil supply hole 24a, it is possible to prevent the lubricating oil from being insufficient during the low-speed rotation even if the swing scroll 32 is enlarged.

Further, as shown in FIG. 3 of the first embodiment, when the oil circulation portion 92 is formed in an arc shape, particularly along the rotation path of the orbiting scroll 32, the reaction force is weakened by the lubricating oil. The effect works, and the movement of the lubricating oil in the oil circulation part 92 can be more efficiently regulated.

The manufacturing method of the scroll compressor 100 of the present embodiment, particularly the processing of the main shell 11 and the arrangement of the fixed scroll 31 and the like will be described in more detail with reference to FIG. FIG. 13 is a diagram for explaining a method of manufacturing the main shell. Note that FIG. 13 illustrates a cross section of one wall of the main shell 11 in an easy-to-understand manner, and is different from actual dimensions and thicknesses.

First, a cutting brush or the like is inserted from one end U of the main shell 11 as shown in (a), the inner wall surface is cut by a predetermined depth in the thickness direction, and the second as shown in (b). A step is formed by the inner wall surface 114 and the second protrusion 115. The thickness of the main shell 11 is, for example, 4 to 6 mm, and the height of the protrusion, that is, the depth of cutting by cutting, is, for example, about 0.3 mm. Next, by cutting the inner wall surface by a predetermined depth in the thickness direction with a cutting brush or the like on the second inner wall surface 114 that is a predetermined distance away from the second protrusion 115 in the direction of the upper shell 12 ( As shown in c), a step is formed by the first inner wall surface 111 and the first protrusion 112. For this reason, the inner diameter r1 of the first inner wall surface 111 is larger than the inner diameter r2 of the second inner wall surface 114. The first protrusion 112 is formed in the direction of the upper shell 12 relative to the second protrusion 115, and the inner wall surface of the first protrusion 112 also serves as the second inner wall surface 114. Note that the second protrusion 115 may be formed after the first protrusion 112 is formed.

In addition, after the cutting processes of (b) and (c), the connection portion (the first inner wall surface 111 side of the first positioning surface 113) of the first protrusion 112 with the first inner wall surface 111, and the second protrusion 115. Dent 1131 having a shape recessed in the direction of the lower shell 13 by processing the outer diameter with a rhombus insert or the like on the connecting portion with the second inner wall surface 114 (on the second inner wall surface 114 side of the second positioning surface 116), 1161 are formed. The

dents

1131 and 1161 are so-called pussies that remove a curved surface that is likely to be generated in the connecting portion by cutting. That is, when cutting is performed, the connection portion between the first inner wall surface 111 and the first positioning surface 113 is not a right angle, and a radius is likely to be formed. If a rounded portion is formed in the portion, even if the fixed scroll 31 is disposed on the first projecting portion 112, it floats without contacting the first positioning surface 113, and the positioning accuracy is lowered. On the other hand, by forming the recess 1131, the fixed scroll 31 reliably contacts the first positioning surface 113, so that the positioning accuracy can be increased. The same applies to the recess 1161, and the positioning accuracy of the main frame 2 can be increased. Since the

recesses

1131 and 1161 are recessed in the direction of the lower shell 13, compared with the case where the recesses are formed in the radial direction of the main shell, it is possible to suppress a decrease in the thickness of the main shell 11. Can be suppressed.

Next, the main frame 2 is inserted from one end side U of the main shell 11 formed as described above. The main frame 2 is in surface contact with the second positioning surface 116 of the second protrusion 115 and is positioned in the height direction. In this state, the main frame 2 is fixed to the second inner wall surface 114 by shrink fitting, arc spot welding, or the like. Then, after inserting the crankshaft 6 into the shaft hole 221 of the main frame 2, the bush 7 is attached to the eccentric shaft portion 62, and the Oldham ring 33, the swing scroll 32, and the like are disposed.

Next, the fixed scroll 31 is inserted from one end U of the main shell 11. The fixed scroll 31 is in surface contact with the first positioning surface 113 of the first protrusion 112 and is positioned in the height direction. In the present embodiment, since there is no member such as a conventional screw for positioning the fixed scroll 31 in the circumferential direction, the fixed scroll 31 is fixed with respect to the orbiting scroll 32 until the fixed scroll 31 is fixed to the first inner wall surface 111. The fixed scroll 31 is rotatable, and the positional relationship between the first spiral body 312 and the second spiral body 322 is shifted, and there is a possibility that a variation in compression or a defective compression occurs in each scroll compressor product. Therefore, the fixed scroll 31 is rotated to adjust the phase so that the positional relationship of the first spiral body 312 with respect to the second spiral body 322 of the orbiting scroll 32 is predetermined, and then the fixed scroll 31 is moved to the first inner wall surface 111. Fix by shrink fitting or arc spot welding.

Finally, after the upper shell 12 is inserted from one end U of the main shell 11, the main shell 11 and the upper shell 12 are fixed by welding, arc spot welding, or the like. At that time, the fixed scroll 31 is inserted into the upper shell 12 so as to be pressed against the first positioning surface 113, and the fixed scroll 31 is fixed to the main shell 11 while maintaining the state. The variation in the height of the intake space 37 is suppressed, the positional accuracy is increased, and the fixed scroll 31 is prevented from shifting in the vertical direction when the scroll compressor is driven. However, since the first protrusion 112 only needs to be positioned at least for manufacturing the fixed scroll 31, the fixed scroll 31 comes into contact with the first positioning surface 113 after the fixed scroll 31 is fixed to the first inner wall surface 111. It is not essential to be. The same applies to the relationship between the main frame 2 and the second protrusion 115.

By the manufacturing method as described above, while realizing the positional accuracy of the main frame 2, the fixed scroll 31 and the orbiting scroll 32 as in the conventional method of connecting the main frame 2 and the fixed scroll 31 with screws or the like, The refrigerant intake space 37 can be enlarged. In addition, since no screws or the like are used, manufacturing can be facilitated.

In the present embodiment, the main frame 2 that slidably holds the orbiting scroll 32, the fixed scroll 31 that forms the compression chamber 34 together with the orbiting scroll 32, and the shell 1 that houses the fixed scroll 31 are provided. The shell 1 has a first inner wall surface 111 and a first protrusion 112 that protrudes from the first inner wall surface 111 and on which the fixed scroll 31 is positioned. The fixed scroll 31 is fixed to the first inner wall surface 111. Therefore, the side surface 3212 located on the outermost side in the radial direction of the orbiting scroll 32 and the inner wall surface of the shell 1 face each other, and the main frame 2 is connected to the side surface 3212 of the second substrate 321 and the inner wall surface of the main shell 11. It becomes a structure which does not interpose between. Therefore, the fixed scroll 31 can be disposed in the shell 1 without forming a peripheral wall for fixing the fixed scroll 31 in the main frame 2, and the refrigerant intake space 37 in which the swing scroll 32 is disposed is enlarged. be able to. Thereby, for example, by increasing the diameters of the second substrate 321 and the thrust plate 24 of the orbiting scroll 32, the sliding area can be increased and the surface pressure due to the thrust load can be reduced. Moreover, since the wall for fixing the fixed scroll 31 to the main frame 2 becomes unnecessary, the processing time of the main frame 2 can be shortened and weight reduction can also be achieved.

The shell 1 further includes a second inner wall surface 114 and a second projecting portion 115 that protrudes from the second inner wall surface 114 and is positioned on the main frame 2. The main frame 2 is fixed to the second inner wall surface 114. Has been. Therefore, both the fixed scroll 31 and the main frame 2 can be fixed to the shell 1 by a similar method in a series of manufacturing steps, and manufacturing can be facilitated.

The second inner wall surface 114 is formed on the inner wall surface of the first protrusion 112. That is, the inner wall surface of the first protrusion 112 also serves as the second inner wall surface 114. Therefore, the 1st protrusion part 112 and the 2nd protrusion part 115 can be formed with few processes. Also, the inner diameter r1 of the first inner wall surface 111 is formed larger than the inner diameter r2 of the second inner wall surface 114, and the shell 1 is an upper covering the main shell 11 having both ends opened and the opening on one end side of the main shell 11. A shell 12 and a lower shell 13 that covers the opening on the other end side of the main shell 11, and a first positioning surface 113 for positioning the fixed scroll 31 is formed on the upper shell 12 side of the first protrusion 112, A first positioning surface 113 is formed, and a second positioning surface 116 for positioning the main frame 2 is formed on the upper shell 12 side of the second protrusion 115. Therefore, since the fixed scroll 31 and the main frame 2 can be fixed to the main shell 11 by the same method, assembly can be facilitated.

The first positioning surface 113 is formed in the direction of the upper shell 12 relative to the sliding surface 3211 of the swing scroll 32 that slides on the main frame 2, and the second positioning surface 116 is lower than the sliding surface 3211. It is formed in 13 directions. Therefore, after the main frame 2 is inserted and fixed to the main shell 11 from the one end side U, the main shell 11 can be sequentially inserted and fixed in the same posture, so that the assembly is facilitated. be able to.

Depressions

1131 and 1161 are formed in the direction of the lower shell at the connection portion of the first protrusion 112 with the first inner wall surface 111 and the connection portion of the second protrusion 115 with the second inner wall surface 114. Therefore, the contact between the first positioning surface 113 and the fixed scroll 31 and the contact between the second positioning surface 116 and the main frame 2 can be kept good, and the positioning accuracy can be increased.

The outer diameter of the upper shell 12 is smaller than the inner diameter on one end side of the main shell 11, and the upper shell 12 sandwiches the fixed scroll 31 between the first protrusions 112. Therefore, the fixed scroll 31 can be pressed so as to be surely brought into contact with the first positioning surface 113. Further, the vertical movement of the fixed scroll 31 with respect to the main shell 11 can be suppressed.

The main frame 2 has a thrust plate 24 that slides with a sliding surface 3211 on a flat surface 212 that faces the orbiting scroll 32, and an outer end of the flat surface 212 of the main frame 2 has an upper shell 12. A protruding wall 216 protruding in the direction is formed, and the height h of the protruding wall 216 from the flat surface 212 is smaller than the thickness d of the thrust plate 24. Therefore, the orbiting scroll 32 can be slid on the thrust plate 24 without interfering with the main frame 2.

Further, the thrust plate 24 and the protruding wall 216 are formed with a convex portion or a concave portion, and the convex portion and the concave portion are engaged so that rotation of the thrust plate can be suppressed. The protrusions are a pair of protrusions 217 formed protruding from the protrusion wall 216 in the direction of the thrust plate 24, the recesses are notches 241 formed in the outer peripheral portion of the thrust plate, and the pair of protrusions 217 are It is provided in the notch 241. Therefore, the thrust plate 24 can be prevented from rotating with respect to the flat surface 212 of the main frame 2. A suction port 213 is formed between the pair of protrusions 217 of the frame so as to penetrate in the direction of the upper shell 12 and the direction of the lower shell 13. Therefore, the suction port 213 can be prevented from being blocked by the thrust plate 24, and the refrigerant can be stably supplied to the refrigerant intake space 37.

A refrigeration cycle apparatus that includes a scroll compressor, a condenser, an expansion valve, and an evaporator, and circulates a refrigerant. A high-pressure refrigerant containing, for example, R32 may be used as the refrigerant. When a high-pressure refrigerant containing R32 or the like is used, the burden on the thrust bearing increases, but in the present embodiment, the diameter of the second substrate 321 and the thrust plate 24 of the orbiting scroll 32 is increased to increase the sliding area. Since it can be increased, the burden on the thrust bearing can be reduced and the reliability can be improved.

<Modification 2>
FIG. 14 is a cross-sectional view of the scroll compressor 100 according to Modification 2 of the present invention, and FIG. In the following embodiments and the like, portions having the same configuration as that of the scroll compressor 100 of FIGS. 7 to 13 are denoted by the same reference numerals and description thereof is omitted.

In Modification 2, the main shell 11A has a stepped shape including a first straight pipe portion 117A, a second straight pipe portion 118A, and a connecting portion 119A. The first straight pipe portion 117A is provided on one end side U of the main shell 11A. The second straight pipe portion 118A has an outer diameter R2 that is smaller than the outer diameter R1 of the first straight pipe portion 117A, and is provided on the other end side L of the first straight pipe portion 117A. The connecting portion 119A changes such that the outer wall surface diameter increases from the second straight pipe portion 118A toward the first straight pipe portion 117A, and connects the first straight pipe portion 117A and the second straight pipe portion 118A. It is out.

As can be seen from FIG. 15, at least a part of the second inner wall surface 114A is formed on the inner wall surface of the connecting portion 119A. That is, the outer wall surface of the connecting portion 119 </ b> A has a shape whose outer diameter changes, but the inner wall has a flat surface along the central axis of the crankshaft 6. In particular, the second inner wall surface 114A is formed to be flush with the inner walls of the first straight pipe portion 117A, the second straight pipe portion 118A, and the connecting portion 119A. A second projecting portion 115A projects from the second inner wall surface 114A on the other end side L of the connecting portion 19, and a second positioning surface 116A is formed on one end side U of the second projecting portion 115A. 11A is fixed to the second inner wall surface 114A while being positioned by the second protrusion 115A. The first inner wall surface 111A is formed on the inner wall surface of the first straight pipe portion 117A.

The processing method of the main shell 11A of the scroll compressor 100 of the present embodiment will be described in more detail with reference to FIG. FIG. 16 is a view for explaining a method of manufacturing the main shell according to the second modification of the present invention. FIG. 16 shows a cross section of one wall of the main shell 11A in an easy-to-understand manner, and is different from actual dimensions and thicknesses.

First, a press machine is inserted from one end side U of the main shell 11A formed in a cylindrical shape as shown in (a), and press processing or the like is performed on the main shell 11A, whereby the first straight pipe as shown in (b). A stepped shape including a portion 117A, a second straight pipe portion 118A, and a connecting portion 119A is formed. Next, a cutting brush or the like is inserted from one end U of the main shell 11A, and a part of the inner wall surfaces of the connecting portion 119A and the second straight pipe portion 118A are cut in the thickness direction, whereby the second inner wall surface 114A. And the level | step difference by 115 A of 2nd protrusion parts is formed. Here, by not cutting the first straight pipe portion 117A, the inner diameter r3 of the connecting portion 119A and the second straight pipe portion 118A after cutting is made smaller than the inner diameter r4 of the first straight pipe portion 117A. Next, by cutting the inner wall surface of the first straight pipe portion 117A by a predetermined depth in the thickness direction from one end side U of the main shell 11A with a cutting brush or the like, the first inner wall surface 111A and the first projecting portion A step due to 112A is formed. As in the present embodiment, after forming the

recesses

1131A, 1161A and the like, the main frame 2, the fixed scroll 31 and the like are sequentially arranged. In this manufacturing method, the cutting for forming two steps on the inner wall surface can be performed independently by the first straight pipe portion 117A, the second straight pipe portion 118A, and the connecting portion 119A. The cutting amount of 11A is only in the range indicated by the dotted line in FIG. 16C, and the time for cutting can be shortened. In addition, the thickness of the first straight pipe portion 117A portion of the first inner wall surface 111A and the thickness of the second straight pipe portion 118A portion of the second inner wall surface 114A can be made comparable, and the main shell is obtained by cutting. It can suppress that thickness of 11A becomes thin locally.

Note that when the second inner wall surface 114A is formed, the inner wall surface r3 of the cutting portion may be cut so as to be substantially the same as the inner wall surface r4 of the inner wall surface of the first straight pipe portion 117A. That is, the second inner wall surface 114A may be formed by making the inner wall surfaces of the first straight pipe portion 117A, the second straight pipe portion 118A, and the connecting portion 119A flush with each other. Since these steps are flush with each other, there is no level difference, so that the main frame 2 can be smoothly inserted from the one end U of the main shell 11A. If it is difficult to cut the inner wall surfaces of the connecting part 119A and the second straight pipe part 118A so as to be substantially the same as the inner diameter r4 of the inner wall surface of the first straight pipe part 117A, the connecting part 119A and the second straight pipe part 118A When cutting the inner wall surface of the two straight pipe portions 118A, the inner wall surface of the first straight pipe portion 117A may be slightly cut to be flush with each other.

In this modification, the main shell 11A includes a first straight pipe portion 117A, a second straight pipe portion 118A having an outer diameter R2 smaller than the outer diameter R1 of the first straight pipe portion 117A, and a first straight pipe portion 117A. A connecting portion 119A for connecting the second straight pipe portion 118A, and at least a part of the second inner wall surface 114A is formed on the inner wall of the connecting portion 119A. Therefore, by cutting the inner wall surface of the connecting portion 119A, the entire second protruding portion 115A or a part thereof can be formed, and the amount to be cut is reduced compared to the case of the normal cylindrical main shell 11A. Can be facilitated.

Further, the first inner wall surface 111A is formed on the inner wall of the first straight pipe portion 117A, and the second inner wall surface 114A is formed on the inner walls of the second straight pipe portion 118A and the connecting portion 119A. Therefore, the first protruding portion 112A is cut by cutting a part of the inner wall surface of the first straight pipe portion 117A, and the second protruding portion 115A is cut by cutting the inner wall surfaces of the connecting portion 119A and the second straight pipe portion 118A. Can be formed. Therefore, the depth of cutting to form the first protruding portion 112A and the second protruding portion 115A can be made substantially the same, and the thickness of the cut first straight pipe portion 117A can be suppressed from becoming too thin. . Further, the second inner wall surface 114A has a sufficient length, and the fixing strength with the main frame 2 can be increased. Note that the inner diameter r3 of the second inner wall surface 114A is smaller than the inner diameter r4 of the first straight pipe portion 117A, and thus has a step shape. However, the step is slight and the shape of the inner wall surface of the connecting portion 119A is tapered. Therefore, when the main frame 2 is inserted from the one end side U of the main shell 11A, the smooth insertion does not suppress the smooth insertion. Therefore, it is possible to easily perform the manufacturing while reducing the amount of shaving to form the second inner wall surface 114A.

<Modification 3>
17 is a cross-sectional view of the scroll compressor 100 according to the third modification of the present invention, and FIG.

In the third modification, the inner diameter of the upper shell 12B is set larger than the outer diameter on one end side of the main shell 11B, and the fixed scroll 31B is positioned on the one end side U of the main shell 11B, and the upper shell 12B It is fixed to the inner wall surface. That is, a step is formed by the main shell 11B and the upper shell 12B, the inner wall surface of the upper shell 12B is the first inner wall surface 111B, the one end U of the main shell 11B is the first protrusion 112B, and the one end of the main shell 11B. The end surface on the side U also serves as the first positioning surface 113B. For this reason, it is not necessary to cut the inner wall surface of the main shell 11B in order to form the first protrusion 112B, and the manufacturing can be facilitated. The fixed scroll 31B can be fixed by screwing to the upper shell 12B, spot welding with the upper shell 12B with a laser or the like, or screwing to the end surface of one end U of the main shell 11B. In consideration of welding the main shell 11B and the upper shell 12B, it is desirable that the upper shell 12B is provided so as to be at least partially inscribed in the main shell 11B.

Further, as shown in FIG. 18, a protruding wall 314B protruding to the other end L is formed on the outer end portion of the first substrate 311B of the fixed scroll 31B. The projecting wall 314B is a projecting piece for positioning the fixed scroll 31B in the radial direction with respect to the main shell 11B. The projecting wall 314B is disposed so that the outer wall surface is in contact with the inner wall surface of the main shell 11B and is fixed by shrink fitting. ing. Thereby, when the fixed scroll 31B is disposed on the first positioning surface 113B, the fixed scroll 31B can be prevented from being displaced in the radial direction with respect to the main shell 11B.

In this modification, the inner diameter of the upper shell 12B is larger than the outer diameter on one end side of the main shell 11B, and the first positioning surface 113B is formed at the end of the main shell 11B on the upper shell 12B side. Thus, it is not necessary to cut the inner wall surface of the main shell 11B in order to form the first protrusion 112B, and the manufacturing can be facilitated.

<Modification 4>
FIG. 19 is a cross-sectional view of a scroll compressor 100 according to Modification 4 of the present invention.

In Modification 4, the first projecting portion 112C is formed in a projecting shape projecting from the first inner wall surface 111C, and the fixed scroll 31C is positioned on the first projecting portion 112C. Therefore, the first protrusion 112C can be easily formed. The first projecting portion 112C can be formed by cutting the first inner wall surface 111C by bonding, or can be formed by adhering a previously formed protruding member to the inner wall surface. The first positioning surface 113C is tapered on the first protrusion 112C, and the inclined surface 315C is also formed on the first substrate 311C of the fixed scroll 31C so that the inclined surfaces are in contact with each other. Therefore, the positioning accuracy of the fixed scroll 31C with respect to the main shell 11C can be increased.

In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably.

For example, although the vertical scroll compressor has been described in the above embodiment, it can also be applied to a horizontal scroll compressor. At that time, even in a horizontal scroll compressor, the side on which the compression mechanism portion is provided can be viewed as one end side and the side on which the drive mechanism portion is provided as the other end side with reference to the main frame. . Further, the present invention is not limited to the low-pressure shell type scroll compressor, and can be applied to a high-pressure shell type scroll compressor in which the pressure in the space in the main shell in which the drive mechanism unit is disposed is higher than the pressure in the refrigerant intake space. In the high-pressure shell system, since the load on the thrust bearing is small, it is desirable to adopt a structure in which the displacement amount is increased as shown in FIG. 13 described later or a structure in which the compressor is reduced in size as shown in FIG.

The main shell 11 is not limited to a cylindrical shape, and may be a polygonal cylinder or the like. Further, in the above-described embodiment, the spiral body has an effect that the refrigerant intake space 37 between the first substrate 311 of the fixed scroll 31 and the thrust bearing of the main frame 2 in the main shell 11 can be expanded as compared with the related art. Although the conventional design is the same, the sliding substrate is increased in diameter by increasing the diameters of the second substrate 321 and the thrust plate 24 of the orbiting scroll 32, and the thrust load is reduced. Absent.

FIG. 20 is a cross-sectional view of a scroll compressor 100 according to Modification 5 of the present invention. For example, as shown in FIG. 20, the diameter of the second substrate 321D of the orbiting scroll 32D is the same as the present embodiment, but the first spiral body 312D of the fixed scroll 31D is further connected to the end of the first substrate 311D. While forming to the vicinity, you may form 2nd spiral body 322D of rocking scroll 32D to the edge part vicinity of 2nd board | substrate 321D. Thereby, since the maximum intake amount of the refrigerant by the scroll, that is, the so-called displacement amount can be increased, the compression ratio can be increased and the performance of the scroll compressor can be improved. In addition, since the FO refrigerant | coolant which is a low GWP refrigerant | coolant, especially HFO1234yf is a refrigerant | coolant with a low density, it is desirable to enlarge the amount of displacement. Therefore, by combining with the configuration of FIG. 13, a scroll compressor with high performance can be realized while suppressing an increase in size.

Note that when the second spiral body 322D and the second substrate 321D of the orbiting scroll 32D are enlarged, the centrifugal force due to the orbiting motion of the orbiting scroll 32D increases due to the weight increase or the like. Therefore, it is necessary to offset the centrifugal force by increasing the volume or weight of the weight portion 721D of the balancer 72D. On the other hand, in the present invention, since the wall for screwing in the main frame 2 is eliminated, the design freedom of the main frame 2D is increased, so that a large accommodation space 211D of the main body 21D of the main frame 2D is secured. can do. Since the balancer 72D having the weight portion 721D having a large volume can be used by enlarging the accommodation space 211D, the centrifugal force of the orbiting scroll 32D, which has become larger due to weighting or the like, is canceled out. The radial load acting on the second spiral body 322 can be reduced. Therefore, the reliability of the orbiting scroll 32 can be improved, and the sliding loss between the second spiral body 322 of the orbiting scroll 32 and the first spiral body 312 of the fixed scroll 31 can be reduced.

Due to the above structure, the reliability of the orbiting scroll 32 is ensured when the scroll compressor 100 is accelerated (high speed rotation), and the scroll rotation is high when the scroll compressor 100 is accelerated (high speed rotation). The sliding loss between the second spiral body 322 of the orbiting scroll 32 and the first spiral body 312 of the fixed scroll 31 can be reduced by the numbering, and the reliability of the scroll compressor 100 can be improved while ensuring reliability and performance. Refrigerating capacity can be expanded by increasing the speed (higher rotation speed).

However, if the speed of the scroll compressor 100 is increased (high rotation speed), the amount of oil supply becomes excessive, leading to a decrease in refrigeration capacity and a decrease in performance as the amount of oil rising increases. However, since the oil supply groove 90 is provided, the reliability of the orbiting scroll 32 can be ensured, the spiral sliding loss can be suppressed, and the refrigerating capacity and the performance can be prevented from decreasing due to the increase in the amount of oil rising. The refrigerating capacity can be expanded by increasing the speed of the compressor 100 (higher rotation speed).

Further, since the structure is as described above, the thrust sliding surface of the swing scroll 32 (and the radial width of the thrust plate 24) can be designed to be larger. Thereby, the design freedom degree of the shape of the oil distribution part 92 increases. For example, the oil circulation part 92 can be formed in a linear shape, an elliptical shape, a polygonal shape, or the like. Further, the selection range of the number of the oil supply groove 90 and the oil supply hole 24a is widened. From these design degrees of freedom, the effect of the oil supply groove 90 is more effectively exhibited.

FIG. 21 is a cross-sectional view of the scroll compressor 100 according to Modification 6 of the present invention. As shown in FIG. 21, the size of the orbiting scroll 32 remains the same, and the shell 1E, that is, the main shell 11E, the upper shell 12E, and the like may have a smaller inner diameter than the conventional one. Thereby, compared with the past, the amount of displacement is equivalent and a small scroll compressor is realizable.

The first protrusion 112 and the first positioning surface 113 can adopt various shapes and manufacturing methods as long as the fixed scroll 31 can be accurately positioned. For example, the first protrusion 112 only needs to be able to position the fixed scroll 31, and thus may be configured by at least two or more protrusions formed on the inner wall surface of the main shell 11. Further, the first protrusion 112 may be formed by hitting from the outside of the main shell 11. A convex portion may be formed on the first positioning surface 113 and fitted into a concave portion formed on the fixed scroll 31 to suppress the rotation of the fixed scroll 31 with respect to the main shell 11.

FIG. 22 is a cross-sectional view of the scroll compressor 100 according to Modification 7 of the present invention. As shown in FIG. 22, the projections or recesses formed on the thrust plate 24F and the projection wall 216F project in the direction of the projection wall 216F on the thrust plate 24F to form a pair of projections 242F, and the projection wall 216F is notched. 218F may be formed, and a pair of protrusions 242F may be disposed in the notch 218F. Thereby, similarly to 1st Embodiment, rotation of the thrust plate 24F can be suppressed.

The thrust plate 24 is not limited to an annular shape, and may have a C shape, and a suction port 213 having a large opening area may be disposed at a portion where the thrust plate 24 is cut. Thereby, the area of the suction port 213 can be expanded. At this time, if the area of the suction port 213 is increased, a part of the suction port 213 may be blocked by the swing scroll 32 depending on the timing of the swing of the swing scroll 32. In this case, if the suction port 213 is not blocked by the swing scroll 32 at the timing when the refrigerant is taken in by the fixed scroll 31 and the swing scroll 32, the influence of the suction port 213 being blocked can be reduced.

The thrust plate 24 is not essential, and the flat surface 212 of the main frame 2 may slide with the orbiting scroll 32.

A convex portion (or concave portion) is formed on the inner wall surface of the main shell 11 in a direction along the central axis of the crankshaft 6, and a concave portion (or convex portion) that engages with the convex portion (or concave portion) of the main frame 2 and the fixed scroll 31. May be formed. Thereby, since the phase of the first spiral body 312 of the fixed scroll 31 and the second spiral body 322 of the swing scroll 32 can be matched, the phase is adjusted by rotating the fixed scroll 31 with respect to the swing scroll 32. The step of performing can be omitted.

Embodiment 3 FIG.
<Refrigeration cycle apparatus 101>
FIG. 23 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 101 to which the scroll compressor 100 according to Embodiment 3 of the present invention is applied.

23, the refrigeration cycle apparatus 101 includes a scroll compressor 100, a condenser 102, an expansion valve 103, and an evaporator 104. The scroll compressor 100, the condenser 102, the expansion valve 103, and the evaporator 104 are connected by a refrigerant pipe to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 104 is sucked into the scroll compressor 100 and becomes high temperature and pressure. The high-temperature and high-pressure refrigerant is condensed in the condenser 102 to become a liquid. The refrigerant that has become liquid is decompressed and expanded by the expansion valve 103 to become a low-temperature and low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 104.

The scroll compressor 100 according to

Embodiments

1 and 2 can be applied to such a refrigeration cycle apparatus 101. Examples of the refrigeration cycle apparatus 101 include an air conditioner, a refrigeration apparatus, or a water heater.

1, 1E shell, 2, 2D main frame, 3 compression mechanism section, 4 drive mechanism section, 5 subframe, 6 crankshaft, 7 bushing, 8 power feeding section, 11, 11A, 11B, 11C, 11E main shell, 11a low pressure Chamber, 12, 12B, 12E Upper shell, 12a High pressure chamber, 13 Lower shell, 14 Suction pipe, 15 Discharge pipe, 16 Connection shell, 17 Fixing base, 19 Connection part, 21, 21D Main body part, 22 Main bearing part, 23 Return Oil pipe, 24, 24F thrust plate, 24a oil supply hole, 25 oil sump space, 31, 31B, 31C, 31D fixed scroll, 32, 32D rocking scroll, 33 Oldham ring, 34 compression chamber, 35 muffler, 36 discharge valve, 37 Refrigerant intake space, 38 discharge holes, 41 stator 42 rotor, 51 auxiliary bearing, 52 oil pump, 61 main shaft, 62 eccentric shaft, 63 oil passage, 64 first balance weight, 65 second balance weight, 71 slider, 72, 72D balancer, 81 cover, 82 Power supply terminal, 83 wiring, 90 oil supply groove, 91 oil inflow section, 92 oil distribution section, 93 oil outflow section, 100 scroll compressor, 101 refrigeration cycle apparatus, 102 condenser, 103 expansion valve, 104 evaporator, 111, 111A, 111B, 111C first inner wall surface, 112, 112A, 112B, 112C first protrusion, 113, 113B, 113C first positioning surface, 114, 114A second inner wall surface, 115, 115A second protrusion, 116, 116A second positioning surface, 117A first straight pipe section, 118A Second straight pipe portion, 119A connecting portion, 211, 211D accommodating space, 212 flat surface, 213 suction port, 214 Oldham accommodating portion, 215 first Oldham keyway, 216, 216F protruding wall, 217 protruding portion, 218F notch, 221 Shaft hole, 241 notch, 242F protrusion, 311, 311B, 311C, 311D first substrate, 312, 312D first spiral, 313 discharge port, 314B protruding wall, 315C inclined surface, 316 seal, 321, 321D second Substrate, 322, 322D, second spiral body, 323, cylindrical portion, 324, second Oldham keyway, 325 seal, 331 ring portion, 332, first key portion, 333, second key portion, 351 discharge hole, 721, 721D weight portion, 1131, 1131A dent, 1161 dent, 1 161A dent, 3211 sliding surface, 3212 side surface.

Claims

A fixed scroll having a fixed spiral body;
An orbiting scroll having an orbiting side spiral body combined with the fixed side spiral body of the fixed scroll; and
A thrust plate that supports the lower surface of the orbiting scroll so as to be able to swing, and has an opening in the center;
With
An oil sump space is formed inside the thrust plate,
A scroll compressor in which a compression chamber for sucking a working fluid to be compressed is formed between the fixed scroll and the swing scroll,
The orbiting scroll is provided on a sliding surface that slides with the thrust plate, and includes an oil supply groove to which lubricating oil is supplied,
The thrust plate has an oil supply hole that leads from the surface that slides with the orbiting scroll to the compression chamber,
The oil supply groove is
An oil inflow section into which lubricating oil flows,
An oil circulation part, one side leading to the oil inflow part and extending from the oil inflow part in the rotation direction of the rocking scroll;
An oil outflow portion that communicates with the other side of the oil circulation portion, and causes the lubricating oil that has passed through the oil circulation portion to flow out to the oil supply hole side when positioned on the oil supply hole;
With
In one rotation in which the swing scroll swings,
A first rotation period in which the oil circulation part is located on the thrust plate and lubricating oil is supplied to the oil supply hole via the oil circulation part;
A second rotation period in which the oil circulation part is positioned on the oil reservoir space, and the amount of lubricating oil supplied to the oil supply hole via the oil circulation part is less than the first rotation period;
Including scroll compressor.
The scroll compressor according to claim 1, wherein an oil outflow portion of the oil supply groove is formed so as to be positioned on the oil supply hole in the first rotation period.
The scroll compressor according to claim 1 or 2, wherein the oil circulation part is formed in an arc shape.
4. The scroll compressor according to claim 3, wherein the oil circulation part is formed along a rotation orbit of the swing scroll.
The scroll compressor according to claim 3 or 4, wherein the oil circulation portion is formed in an obtuse arc shape along a circumferential direction between an outer periphery and an inner periphery of the swing scroll.
A frame for slidably holding the swing scroll;
An Oldham ring provided between the frame and the orbiting scroll to restrict the rotation of the orbiting scroll;
Further comprising
The Oldham ring includes an Oldham key protruding to the swing scroll side,
The orbiting scroll has an Oldham key groove into which the Oldham key is fitted,
The scroll compressor according to any one of claims 1 to 5, wherein the oil inflow portion communicates with the Oldham key groove, and the lubricating oil in the Oldham key groove flows into the oil inflow portion.
A pair of Oldham key grooves are provided symmetrically with respect to a predetermined radius of the orbiting scroll,
The scroll compressor according to claim 6, wherein the oil supply hole is formed in the vicinity of the other side opposite to one of the pair of Oldham key grooves connected to the oil inflow portion.
The scroll compressor according to any one of claims 1 to 7, wherein a plurality of the oil supply holes of the thrust plate and the oil supply grooves of the swing scroll are provided.
The scroll compressor according to claim 8, wherein two oil supply holes of the thrust plate and two oil supply grooves of the orbiting scroll are provided.
10. The oil supply hole of the thrust plate and the oil supply groove of the orbiting scroll are respectively provided in two symmetrically with respect to a predetermined radius of the thrust plate and the orbiting scroll. Scroll compressor.
A frame for slidably holding the swing scroll;
A shell containing the frame and the fixed scroll;
Further comprising
The shell has a first inner wall surface, and a first projecting portion that projects from the first inner wall surface and positions the fixed scroll,
The scroll compressor according to any one of claims 1 to 10, wherein the fixed scroll is fixed to the first inner wall surface.
12. The scroll compressor according to claim 11, wherein the orbiting scroll has a side surface located at an outermost portion in a radial direction, and the side surface and an inner wall surface of the shell face each other.
The shell further includes a second inner wall surface, and a second projecting portion that projects from the second inner wall surface and positions the frame,
The scroll compressor according to claim 11 or 12, wherein the frame is fixed to the second inner wall surface.
The scroll compressor according to claim 13, wherein the second inner wall surface is formed on an inner wall surface of the first projecting portion.
The scroll compressor according to claim 13 or 14, wherein an inner diameter of the first inner wall surface is formed larger than an inner diameter of the second inner wall surface.
The shell includes a main shell having both ends opened, a first shell covering an opening on one end side of the main shell, and a second shell covering an opening on the other end side of the main shell,
A first positioning surface for positioning the fixed scroll is formed on the first shell side of the first protrusion,
The scroll compressor according to claim 13, wherein a second positioning surface for positioning the frame is formed on the first shell side of the second protrusion.
The first positioning surface is formed in the direction of the first shell from the sliding surface of the orbiting scroll that slides with the frame,
The scroll compressor according to claim 16, wherein the second positioning surface is formed in a direction of the second shell with respect to the sliding surface.
The main shell connects the first straight pipe part, the second straight pipe part having an outer diameter smaller than the outer diameter of the first straight pipe part, and the first straight pipe part and the second straight pipe part. A connecting portion,
The scroll compressor according to claim 13, wherein at least a part of the second inner wall surface is formed on an inner wall of the connecting portion.
The first inner wall surface is formed on the inner wall of the first straight pipe portion,
The scroll compressor according to claim 18, wherein the second inner wall surface is formed on at least a part of the second straight pipe portion and an inner wall of the connecting portion.
The scroll compressor according to claim 18 or 19, wherein an inner diameter of the second inner wall surface is formed smaller than an inner diameter of the first straight pipe portion.
A recess is formed in the direction of the second shell in at least one of a connection portion with the first inner wall surface in the first protrusion and a connection portion with the second inner wall surface in the second protrusion. The scroll compressor according to any one of claims 16 to 20.
The outer diameter of the first shell is formed smaller than the inner diameter of the one end side of the main shell,
The scroll compressor according to any one of claims 16 to 21, wherein the first shell sandwiches the fixed scroll with the first protrusion.
The inner diameter of the first shell is formed larger than the outer diameter of the one end side of the main shell,
The scroll compressor according to any one of claims 16 to 21, wherein the first positioning surface is formed at an end of the main shell on the first shell side.
The frame has the thrust plate that slides with the sliding surface on a flat surface facing the orbiting scroll,
A protruding wall protruding in the direction of the first shell is formed at the outer end of the flat surface of the frame,
The scroll compressor according to claim 16, wherein a height of the protruding wall from the flat surface is smaller than a thickness of the thrust plate.
A convex part or a concave part is formed on the thrust plate and the protruding wall,
The scroll compressor according to claim 24, wherein the convex portion and the concave portion are engaged so that rotation of the thrust plate can be suppressed.
The convex portion is a pair of protrusions,
The recess is a notch;
The scroll compressor according to claim 25, wherein the pair of protrusions are provided in the notches.
The scroll compressor according to claim 26, wherein a suction port is formed in the frame so as to penetrate a portion between the pair of protrusions.
A refrigeration cycle apparatus comprising the scroll compressor according to any one of claims 1 to 27.
A refrigeration cycle apparatus comprising the scroll compressor, a condenser, an expansion valve, and an evaporator, and circulating a refrigerant as a working fluid,
The refrigeration cycle apparatus according to claim 28, wherein the refrigerant includes R32 or HFO refrigerant.