JP6118702B2 - Scroll compressor and refrigeration equipment - Google Patents

Description

  The present invention relates to a scroll compressor and a refrigeration apparatus including the same.

  In the scroll compressor, a change close to the adiabatic change in compression of the fluid occurs between the scroll wraps, so the temperature level of both scroll wraps during operation is different from the other parts, and the thermal expansion amount differs from the other parts. Occurs. A fixed scroll has more contact with parts other than a turning scroll compared with a turning scroll, and free thermal expansion is prevented in a contact part. For this reason, during operation, the size of the orbiting scroll (end plate part) changes relative to the fixed scroll, and the temperature rises and the orbiting scroll lap thermally expands. Thereby, the side clearance between the orbiting scroll wrap and the fixed scroll wrap becomes small, and there is a possibility that both scroll laps interfere with each other.

In order to avoid such interference between both scroll wraps, the amount of eccentricity of the orbiting scroll is set smaller than the amount determined from the shape of the scroll wrap. As a result, the side gap between the scroll wraps is enlarged, and the assembly accuracy of the orbiting scroll and the fixed scroll is varied, causing a decrease in the average performance level.
As the above countermeasure, there is one disclosed in Patent Document 1.

  In this scroll compressor, the side gap formed by the orbiting scroll wrap and the fixed scroll wrap is made smaller in the section closer to the center from the center winding start point than in the section closer to the outer periphery than the center section. As a structure, the wrap thickness of the orbiting scroll wrap is achieved by making the wrap thickness of the orbiting scroll wrap thicker than the wrap thickness in the section from the center to the outer periphery in the section closer to the center from the winding start point. As a result, the assembly accuracy is improved and a decrease in the average performance level is suppressed.

Japanese Patent No. 3747358

  The compression chamber formed by the orbiting scroll and the fixed scroll has two compression chambers, an orbiting scroll inner line side compression chamber and an orbiting scroll outer line side compression chamber, and both compression chambers have side gaps. In Patent Document 1, the wrap thickness of the orbiting scroll wrap is structured such that the amount of thickening is the same, with the orbiting scroll wrap inner line side inward and the orbiting scroll wrap outer line side outward. That is, the gaps on the side surfaces of both the compression chambers are in a uniform gap state on the inner line side and the outer line side of the orbiting scroll.

  By the way, in a scroll compressor, an intermediate pressure or a discharge pressure, which is a pressure between the suction pressure and the discharge pressure, is pressed against the back of the end plate portion where the orbiting scroll wrap is erected, thereby pressing the orbiting scroll against the fixed scroll. A compression chamber is formed to perform the compression operation. If this pressing force is weak, the orbiting scroll will oscillate, and the refrigerant gas compressed from the end of the orbiting scroll lap will leak to the lower compression chamber side, increasing the leakage loss and greatly reducing performance. Will be. On the other hand, when the pressing force is strong, the leakage of the refrigerant gas from the wrap tip is suppressed, but the sliding loss of the wrap tip increases, and the performance is significantly lowered. The pressing force is designed in consideration of these leakage loss and sliding loss.

  In recent years, the carbon dioxide refrigerant used in heat pump water heaters and the like has been operated under high temperature and high pressure conditions, and the pressing force of the orbiting scroll is larger than the R410A refrigerant for room air conditioners in order to improve the performance of the compressor. It is necessary to press against.

FIG. 10 is a cross-sectional view showing deformation of the orbiting scroll 3 during operation. In FIG. 10, the side (front surface) of the orbiting scroll wrap 3 b is illustrated as the upper side, and the side (rear surface) of the orbiting bearing 3 c is illustrated as the lower side. Here, the surface side of the end plate portion 3a, the vicinity of the outer peripheral side of the suction chamber is formed suction pressure P _1, and the the vicinity of the center side becomes the discharge pressure _{P 2 (P 2> P 1} ). On the other hand, the back side of the end plate portion 3a, in the orbiting bearing 3c is near the center side, at a pressure P ₃ by the hydraulic pressure of the lubricating oil flowing through the crankshaft (P ₃ ≒ P ₂₎ pressed, the outer peripheral side near the back-pressure chamber Is pressed at an intermediate pressure P ₄ (P ₁ <P ₄ <P ₂ ). Therefore, the end plate portion 3a of the orbiting scroll 3 is deformed into a bowl shape by these pressing forces as shown in FIG. Furthermore, by this bowl-shaped deformation, the orbiting scroll wrap 3 b standing on the end plate part 3 a is deformed toward the center of the orbiting scroll 3.

  In the gap state of Patent Document 1, due to the above deformation, the side gap between the orbiting scroll wrap inner line side and the fixed scroll wrap outer line side is narrowed, and the side gap between the orbiting scroll wrap outer line side and the fixed scroll wrap inner line side is enlarged. It becomes. In addition, in the high-temperature and high-pressure carbon dioxide refrigerant, the differential pressure between the compression chambers is large. Therefore, in the portion where the side gap is enlarged, the refrigerant gas leaks to the low compression chamber side, resulting in significant leakage loss. It will increase and the performance will drop significantly.

  Then, this invention makes it a subject to provide a high performance and highly reliable scroll compressor and a refrigeration apparatus provided with the same.

In order to solve such a problem, a scroll compressor according to the present invention includes a turning scroll having a turning scroll wrap, a fixed scroll having a fixed scroll wrap, an inner line of the turning scroll wrap, and an outer line of the fixed scroll wrap. And a second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap, and the swirl that is a side clearance of the first compression chamber A side gap between the inner line of the scroll wrap and the outer line of the fixed scroll wrap is δA, and a side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap, which is the side gap of the second compression chamber, is δB. when, as .delta.A> .delta.B, the fixed scroll wrap is formed along a fixed wrap centerline, the fixed Tsu than the width of the flops centerline to outside line of the fixed scroll wrap, more from the fixed wrap centerline of the width of up to extension of the fixed scroll wrap, being greater.
Moreover, the scroll compressor which concerns on this invention is the 1st compression formed by the turning scroll which has a turning scroll wrap, the fixed scroll which has a fixed scroll wrap, the inner line of the said turning scroll wrap, and the outer line of the said fixed scroll wrap. A second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap, and the inner line of the orbiting scroll wrap and the fixed scroll that are side gaps of the first compression chamber When the side gap between the outer line of the wrap is δA, and the side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap is the side gap of the second compression chamber, δA> δB, The orbiting scroll wrap is formed along the center line of the orbiting wrap, and the orbiting scroll wrap is formed from the center line of the orbiting wrap. Than the width of up to extension of the roll wraps, the better from the orbiting wrap center line of the width of up to an outside line of the orbiting scroll wrap, being greater.
Moreover, the scroll compressor which concerns on this invention is the 1st compression formed by the turning scroll which has a turning scroll wrap, the fixed scroll which has a fixed scroll wrap, the inner line of the said turning scroll wrap, and the outer line of the said fixed scroll wrap. A second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap, and the inner line of the orbiting scroll wrap and the fixed scroll that are side gaps of the first compression chamber When the side gap between the outer line of the wrap is δA, and the side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap is the side gap of the second compression chamber, δA> δB, The orbiting scroll has an orbiting bearing that fits with an eccentric part of the crankshaft, and the axis of the orbiting bearing and the eccentric part When the clearance is C, characterized by the δA-δB <C.

Moreover, the refrigeration equipment according to the present invention includes a refrigerant circuit including the scroll compressor, a condenser, a decompression unit, and an evaporator.
It is.

  ADVANTAGE OF THE INVENTION According to this invention, a highly efficient and highly reliable scroll compressor and a refrigeration apparatus provided with the same can be provided.

It is a longitudinal cross-sectional view of the scroll compressor which concerns on 1st Embodiment. It is a figure explaining a turning scroll and a fixed scroll, and is a figure which looked at the end plate part of the turning scroll, and saw the turning scroll wrap and the fixed scroll of the turning scroll from the lower side to the upper side in FIG. It is the figure which looked at the fixed scroll with which the scroll compressor which concerns on 1st Embodiment is equipped from the lower side of FIG. In the scroll compressor which concerns on 1st Embodiment, it is the elements on larger scale of the D section of FIG. (A) and (b) are during assembly, and (c) and (d) are during operation. Moreover, (a) and (c) show the side gap of the orbiting scroll inner line side compression chamber, and (b) and (d) show the side gap of the orbiting scroll outer line side compression chamber. It is the figure which looked at the rotating scroll with which the scroll compressor which concerns on 2nd Embodiment is provided seeing through the end plate part of the turning scroll (it shows with a dashed-two dotted line) from the lower side of FIG. In the scroll compressor which concerns on 2nd Embodiment, it is the elements on larger scale of the D section of FIG. (A) and (b) are during assembly, and (c) and (d) are during operation. Moreover, (a) and (c) show the side gap of the orbiting scroll inner line side compression chamber, and (b) and (d) show the side gap of the orbiting scroll outer line side compression chamber. It is the figure which looked at the turning scroll with which the scroll compressor which concerns on 3rd Embodiment is provided seeing through the end plate part of the turning scroll (it shows with a dashed-two dotted line) from the lower side of FIG. It is the figure which looked at the fixed scroll with which the scroll compressor which concerns on 4th Embodiment is equipped from the lower side of FIG. It is a block diagram of the structure of the refrigeration equipment (heat pump type water heater) according to the present embodiment. It is sectional drawing which shows a deformation | transformation of the turning scroll at the time of driving | operation.

  Hereinafter, modes for carrying out the present invention (hereinafter referred to as “embodiments”) will be described in detail with reference to the drawings as appropriate. In each figure, common portions are denoted by the same reference numerals, and redundant description is omitted.

<< First Embodiment >>
<Scroll compressor>
First, the scroll compressor 50 according to the first embodiment will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of a scroll compressor 50 according to the first embodiment.

  As shown in FIG. 1, the scroll compressor 50 includes a sealed container 1, a compression mechanism unit 2 including a revolving scroll 3, a fixed scroll 4, a frame 5, a crankshaft 6 and an Oldham ring 7, an electric motor unit 8, And a bearing 9.

The sealed container 1 is configured such that a lid chamber 1b is welded to the upper side of a cylindrical case 1a and a bottom chamber 1c is welded to the lower side of the cylindrical case 1a. The lid chamber 1b is provided with a suction pipe 1d, and the case 1a is provided with a discharge pipe 1e.
Further, the lid chamber 1b is provided with a terminal 1f for supplying electric power to the electric motor unit 8 disposed inside the sealed container 1. A compression mechanism unit 2 is disposed in the upper part of the sealed container 1 composed of the case 1a, the lid chamber 1b, and the bottom chamber 1c, and an electric motor unit 8 is disposed in the lower part of the sealed container 1. And the machine oil 13 (lubricating oil, refrigerator oil) is stored in the bottom part of the airtight container 1. FIG.

  The compression mechanism unit 2 includes a turning scroll 3, a fixed scroll 4, a frame 5, a crankshaft 6, and an Oldham ring 7.

  The orbiting scroll 3 includes an end plate portion 3a, a spiral orbiting scroll wrap 3b that stands upright on the surface side of the end plate portion 3a (upper side in FIG. 1), and a crankshaft on the rear side (lower side in FIG. 1) of the end plate portion 3a. And 6 slewing bearings 3c to which the eccentric portions 6b are fitted. The fixed scroll 4 includes an end plate portion 4a and a spiral fixed scroll wrap 4b that stands upright on the lower side of the end plate portion 4a (the lower side in FIG. 1). The orbiting scroll 3 is rotatably disposed opposite to the fixed scroll 4, and a suction chamber 15 (see FIG. 2 described later) and a compression chamber 16 (see FIG. 2 described later) are formed by both. .

In addition, a suction port 4 c that communicates with a suction chamber 15 (see FIG. 2 described later) is provided on the outer peripheral portion of the fixed scroll 4. The suction port 4c is formed to extend vertically from the upper surface (anti-wrap surface) of the end plate portion 4a. A suction pipe 1d is press-fitted into the upper part of the suction port 4c. A check valve 10 is disposed in the suction port 4c.
A discharge port 4 d is formed at the center of the fixed scroll 4.

  The frame 5 is fixed to the fixed scroll 4 with a fastener such as a bolt, and supports the orbiting scroll 3 disposed between the fixed scroll 4 and the frame 5. The outer peripheral side of the frame 5 is fixed to the inner wall surface of the sealed container 1 by welding, and includes a main bearing 5a that rotatably supports the main shaft 6a of the crankshaft 6. A back pressure chamber 17 is formed between the orbiting scroll 3 and the frame 5.

  The Oldham ring 7 is disposed between the lower surface side of the orbiting scroll 3 and the frame 5, and is attached to a groove formed on the lower surface side of the orbiting scroll 3 and a groove formed on the frame 5. The Oldham ring 7 functions to make a turning motion by receiving the eccentric rotation of the eccentric portion 6 b of the crankshaft 6 without rotating the orbiting scroll 3.

  The electric motor unit 8 includes a rotor 8a and a stator 8b. The stator 8b is fixed to the sealed container 1 by press fitting, welding, or the like. The rotor 8a is rotatably disposed in the stator 8b. A crankshaft 6 is fixed to the rotor 8a.

  As described above, the crankshaft 6 includes the main shaft 6a and the eccentric portion 6b. The main shaft 6 a of the crankshaft 6 is supported by a main bearing 5 a provided on the frame 5 on the upper side and supported by a lower bearing 9 on the lower side. The eccentric portion 6 b of the crankshaft 6 is formed integrally with the main shaft 6 a so as to be eccentric, and is fitted to the orbiting bearing 3 c provided on the back surface of the orbiting scroll 3. When the electric motor unit 8 is driven to rotate the main shaft 6a, the eccentric portion 6b rotates eccentrically with respect to the main shaft 6a, and the orbiting scroll 3 rotates. Further, the crankshaft 6 is provided with an oil supply passage 6c that guides the machine oil 13 to the main bearing 5a, the lower bearing 9 and the slewing bearing 3c, and an oil supply piece 6d that sucks the machine oil 13 and guides it to the oil supply passage 6c at the lower shaft end. Is installed.

  The fixed scroll 4 is provided with a back pressure valve 11 for controlling the pressure in the back pressure chamber 17. The fixed scroll 4 has a compression chamber 16 (see FIG. 2 to be described later) when a large amount of liquid refrigerant is sucked, such as at startup, or when the pressure ratio “discharge pressure / suction pressure” is low. A release valve 12 for discharging the refrigerant gas to the discharge pressure chamber 18 is provided before the reference) communicates with the discharge port 4d.

Here, the compression action of the scroll compressor 50 will be described.
The rotor 8a rotates with a rotational force applied by a rotating magnetic field generated by the stator 8b. The crankshaft 6 fixed to the rotor 8a rotates as the rotor 8a rotates. The orbiting scroll 3 connected to the crankshaft 6 is orbited (revolved) without rotating due to the action of the Oldham ring 7.

  The check valve 10 opens the suction port 4c by the orbiting motion of the orbiting scroll 3, and the refrigerant gas passes from the suction pipe 1d through the suction port 4c and the suction chamber 15 (see FIG. 2 described later), and then the orbiting scroll 3 and the fixed scroll 4. Is led to a compression chamber 16 (see FIG. 2 described later). Then, the refrigerant gas in the compression chamber 16 (see FIG. 2 described later) is compressed by reducing the volume as it moves in the central direction between the orbiting scroll 3 and the fixed scroll 4. The compressed refrigerant gas is discharged from the discharge port 4d of the fixed scroll 4 to the discharge pressure chamber 18 which is a space in the sealed container 1, and flows out to the outside through the discharge pipe 1e.

  Further, the machine oil 13 stored at the bottom of the closed container 1 is caused by a differential pressure between the discharge pressure of the discharge pressure chamber 18 in the closed container 1 and the back pressure chamber 17 which is an intermediate pressure between the discharge pressure and the suction pressure. The revolving bearing 3c of the orbiting scroll 3 is lubricated and supplied to the back pressure chamber 17 via the refueling piece 6d and the oil supply passage 6c of the crankshaft 6. A part of the machine oil 13 flowing through the oil supply passage 6c is also supplied to the main bearing 5a and the lower bearing 9 of the frame 5, and lubricates each bearing. The machine oil 13 that has flowed into the back pressure chamber 17 is decompressed in the back pressure chamber 17, whereby a part of the refrigerant dissolved in the machine oil 13 is separated. Therefore, the inside of the back pressure chamber 17 is in a gas-liquid mixed state of the refrigerant and the machine oil 13. The machine oil 13 and the refrigerant that have flowed into the back pressure chamber 17 finally flow out from the back pressure valve 11 provided in the fixed scroll 4, and are supplied to the compression chamber 16 (see FIG. 2 described later) to swirl with the fixed scroll 4. Lubricate the scroll 3 and seal each gap.

  In this manner, the orbiting scroll 3 has a hydraulic pressure of the machine oil 13 that is supplied to the orbiting bearing 3 c via the oil supply passage 6 c of the crankshaft 6 (corresponding to the discharge pressure of the discharge pressure chamber 18), and the back pressure chamber 17. The intermediate scroll is pressed against the fixed scroll 4.

<< Compression mechanism 2 (orbiting scroll 3, fixed scroll 4) >>
Next, the compression mechanism unit 2 of the scroll compressor 50 according to the first embodiment will be further described with reference to FIGS. FIG. 2 is a diagram for explaining the orbiting scroll 3 and the fixed scroll 4. The end scroll portion 3 a of the orbiting scroll 3 is seen through the end plate portion 3 a of the orbiting scroll 3, and the orbiting scroll wrap 3 b and the fixed scroll 4 of FIG. FIG.

  As shown in FIG. 2, the orbiting scroll wrap 3b of the orbiting scroll 3 is formed by an orbiting scroll wrap outer line 33a and an orbiting scroll wrap inner line 33b. The fixed scroll wrap 4b is formed by a fixed scroll wrap outer line 44a and a fixed scroll wrap inner line 44b.

  The suction port 4 c of the fixed scroll 4 communicates with the suction chamber 15. By turning the orbiting scroll 3, the space between the orbiting scroll wrap 3b and the fixed scroll wrap 4b is closed, and a part of the suction chamber 15 becomes the compression chamber 16 surrounded by the orbiting scroll wrap 3b and the fixed scroll wrap 4b. . In addition, although the side clearance gap has arisen between the turning scroll wrap 3b and the fixed scroll wrap 4b, it is sealed with the machine oil 13 (refer FIG. 1). Then, when the orbiting scroll 3 is further swung, the compression chamber 16 moves in the center direction, the volume is reduced accordingly, and the refrigerant gas in the compression chamber 16 is compressed. When the compression chamber 16 communicates with the discharge port 4d provided on the center side of the fixed scroll 4, the compressed refrigerant gas in the compression chamber 16 is discharged from the discharge port 4d to the discharge pressure chamber 18 (see FIG. 1). To do.

  The compression chamber 16 includes the orbiting scroll inner line side compression chamber 16a (first compression chamber) formed when the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a are closed, and the orbiting scroll wrap outer line 33a and the fixed scroll. There is a turning scroll outer line side compression chamber 16b (second compression chamber) formed when the wrap inner line 44b is closed.

As described above, the side clearance between the orbiting scroll wrap 3b and the fixed scroll wrap 4b that seals the compression chamber 16 and the other compression chamber 16 (or the suction chamber 15) is the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a. Side surface gaps (δA ₁ , δA ₂ ; see FIG. 4 described later) and side surface clearances (δB ₁ , δB ₂ ; see FIG. 4 described later) between the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b. .

  The fixed scroll 4 of the scroll compressor 50 according to the first embodiment will be further described with reference to FIG. FIG. 3 is a view of the fixed scroll 4 provided in the scroll compressor 50 according to the first embodiment as viewed from the lower side to the upper side in FIG.

  As shown in FIG. 3, the fixed scroll wrap 4b of the scroll compressor 50 according to the first embodiment has a thick wall portion so that the fixed scroll wrap inner line 44b is thicker than the fixed scroll wrap outer line 44a. 44 bt is provided.

In other words, from the amount of eccentricity of the eccentric portion 6b of the crankshaft 6 (the amount of eccentricity of the orbiting scroll 3), the basic thickness of the fixed scroll wrap 4b, and the like, the wrap center line L ₄ (for example, the involute curve) of the fixed scroll wrap 4b is is set, with a width equal to the inside and outside of the lap center line L _4, the basic thickness of the stationary scroll wrap 4b is designed. The fixed scroll wrap 4b of the scroll compressor 50 according to the first embodiment is thicker on the side of the fixed scroll wrap inner line 44b than the basic thickness (a thick portion 44bt is provided). Therefore, than the width of the lap center line L ₄ to the fixed scroll wrap external 44a, towards the width from the lap center line L ₄ to the fixed scroll wrap extension 44b it is larger.

  FIG. 4 is a partial enlarged cross-sectional view of a portion D in FIG. 1 in the scroll compressor 50 according to the first embodiment. (A) and (b) are during assembly, and (c) and (d) are during operation. Further, (a) and (c) show the side gap (side gap between the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a) of the orbiting scroll inner line side compression chamber 16a (see FIG. 2). d) shows a side gap (side gap between the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b) of the orbiting scroll outer line side compression chamber 16b (see FIG. 2). 4A to 4D, the left side is the center side of the orbiting scroll 3 and the fixed scroll 4, and the right side is the outer peripheral side of the orbiting scroll 3 and the fixed scroll 4.

  Here, the time of assembly indicates a state in which the scroll compressor 50 (the orbiting scroll 3 and the fixed scroll 4) is assembled. The assembly time may be a design time, when the scroll compressor 50 is not in operation (no load state. The pressure difference between the front and back surfaces of the end plate portion 3a is small, and the bowl-shaped deformation as shown in FIG. It may be in a state where it does not occur.

  In operation, the scroll compressor 50 is in a compression operation. During operation, the orbiting scroll 3 is strongly pressed against the fixed scroll 4 (pressure load state. Due to the pressure difference between the front and back surfaces of the end plate portion 3a, the bowl-shaped deformation as shown in FIG. 10 occurs. It is good also as a state.).

As shown in FIGS. 4A and 4B, at the time of assembly, the side clearance δA ₁ formed by the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a, the orbiting scroll wrap outer line 33a and the fixed scroll are assembled. The relationship of the formula (1) is established with the side surface gap δB ₁ formed by the wrap extension line 44b.
Side gap δA ₁ > side gap δB ₁ (1)

Further, when the bearing clearance between the orbiting bearing 3c of the orbiting scroll 3 and the eccentric portion 6b of the crankshaft 6 is C, the relationship of Expression (2) is established.
Side clearance δA ₁ −side clearance δB ₁ <Bearing clearance C (2)

In other words, the side gap δB ₁ is smaller than the side gap δA ₁ by providing the thick portion 44 bt in the fixed scroll wrap extension 44 b. Further, the thickness of the thick portion 44bt (corresponding to “side gap δA ₁ -side gap δB ₁ ”) is made smaller than the bearing clearance C between the slewing bearing 3c and the eccentric portion 6b.

  On the other hand, as shown in FIGS. 4 (c) and 4 (d), during operation, the orbiting scroll wrap 3b causes the fixed scroll wrap 4b side (orbiting scroll 3 and It will be deformed to the center side of the fixed scroll 4).

  Here, the deformation mechanism will be described with reference to FIG. FIG. 10 is a cross-sectional view showing deformation of the orbiting scroll 3 during operation. In FIG. 10, the side (front surface) of the orbiting scroll wrap 3 b is illustrated as the upper side, and the side (rear surface) of the orbiting bearing 3 c is illustrated as the lower side.

Surface side of the end plate portion 3a, inlet 4c and the suction chamber 15 (see FIG. 2) is the outer circumferential side near the suction pressure P ₁ becomes to be formed of the fixed scroll 4, a fixed scroll 4 discharge port 4d (see FIG. 2) The vicinity of the center side where is formed is the discharge pressure P ₂ (P ₂ > P ₁ ). Meanwhile, the rear side of the end plate portion 3a, at a pivot bearing 3c is near the center side, the hydraulic by a pressure P ₃ of the machine oil 13 flowing in the oil supply passage 6c of the crankshaft 6 (see FIG. 1) (see FIG. 1) (P ₃ ≒ _{P 2)} pressed, the vicinity of the outer peripheral side are pressed by the back pressure chamber 17 (intermediate pressure _{P 4 (P 1 <P 4} <P 2 in FIG. 1)).

In this way, the orbiting scroll 3 has a pressure P ₃ (discharge pressure chamber 18 (see FIG. 1) due to the hydraulic pressure of the machine oil 13 (see FIG. 1) supplied to the orbiting bearing 3 c via the oil supply passage 6 c (see FIG. 1) of the crankshaft 6. corresponding to the discharge pressure _{P 2} in FIG. 1)), and, by the intermediate pressure _{P 4} in the back pressure chamber 17 (see FIG. 1), it is pressed against the fixed scroll 4 (see FIG. 1). Further, the pressure difference between the front surface and the back surface of the end plate portion 3a is larger on the outer peripheral side than on the center side of the orbiting scroll 3.

  Further, the end plate portion 3a of the orbiting scroll 3 has a structure (orbiting scroll wrap 3b and orbiting bearing 3c) that functions as a rib for suppressing deformation standing on the center side, whereas on the outer peripheral side thereof. Since there are few standing structures, the rigidity of the outer peripheral side of the end plate portion 3a is lowered.

  Therefore, when operating under a high temperature and high pressure condition such as a carbon dioxide refrigerant, the end plate portion 3a of the orbiting scroll 3 is deformed into a bowl shape by these pressing forces as shown in FIG. Further, by the deformation of the bowl shape, the orbiting scroll wrap 3b standing on the end plate portion 3a is deformed toward the center of the orbiting scroll 3 (to the fixed scroll wrap outer line 44a side of the fixed scroll wrap 4b). It will be.

  Returning to FIGS. 4C and 4D, during operation, the end plate portion 3a is deformed by the pressure load, and the orbiting scroll wrap 3b is deformed toward the fixed scroll wrap outer line 44a. Side clearance δB between scroll wrap outer line 33a and fixed scroll wrap inner line 44b is enlarged.

  For this reason, in the conventional scroll compressor, “side clearance δA <side clearance δB”, and the refrigerant gas leaks to the low compression chamber side in the side clearance δB between the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b. Leakage loss can be greatly increased and performance can be significantly reduced.

On the other hand, the scroll compressor 50 according to the first embodiment increases the thickness of the side of the fixed scroll wrap inner line 44b of the fixed scroll wrap 4b (provides a thick portion 44bt), thereby providing a side clearance δB during assembly. ₁ can be narrowed, and the side clearance δB ₂ during operation can also be narrowed. As a result, the side gap δB ₂ can be made substantially equal to the side gap δA ₂ .

In other words, the side clearance .delta.B ₂ during operation, such that the side clearance .delta.A ₂ substantially equal during operation, provided with a thick portion 44bt the fixed scroll wrap extension 44b of the stationary scroll wrap 4b. Note that the side gaps δA ₂ and δB ₂ during operation may be the average of the side gaps, the minimum value of the side gaps, or the maximum value of the side gaps.

Thus, by making the side surface gap δB ₂ substantially equal to the side surface gap δA ₂ , leakage in the orbiting scroll outer line side compression chamber 16b (see FIG. 2) formed by the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b. Loss can be reduced, and the high-performance and high-reliability scroll compressor 50 can be obtained.

Further, as shown in the equation (2), the difference between the side clearance δA ₁ and the side clearance δB ₁ is made smaller than the bearing clearance C between the slewing bearing 3c and the eccentric portion 6b. Thereby, since the centering operation at the time of assembling the orbiting scroll 3 and the fixed scroll 4 secures less than the bearing clearance C, it is possible to maintain the same assembly accuracy as before without causing a centering failure.

Further, when operating under a high temperature and high pressure condition such as a carbon dioxide refrigerant, as a countermeasure against the end plate portion 3a of the orbiting scroll 3 being deformed into a bowl shape (see FIG. 10), conventionally, the end plate portion 3a is thickened. It corresponded. For this reason, the weight of the orbiting scroll 3 that orbits is increased, the power consumption of the electric motor unit 8 is increased, and there is a problem that vibration and noise increase particularly during high-speed rotation. On the other hand, the scroll compressor 50 according to the first embodiment has the side gaps δA ₁ and δB ₁ considering the deformation of the end plate portion 3a of the orbiting scroll 3 without increasing the end plate portion 3a of the orbiting scroll 3. It is possible to reduce the weight of the orbiting scroll 3, suppress an increase in power consumption of the motor unit 8, and suppress vibration and noise during high-speed rotation.

  In addition, the thickness of the end plate portion 3a of the orbiting scroll 3 of the first embodiment is the same as that used in a refrigerant having a lower working pressure than the carbon dioxide refrigerant (for example, a refrigerant mixed with R410A refrigerant, R32 refrigerant, and R32 refrigerant). A thickness equivalent to the end plate portion of the scroll compressor can be secured, and it is not necessary to make significant changes to the processing equipment and assembly equipment.

  Furthermore, by increasing the wrap thickness of the fixed scroll wrap 4b, the rigidity of the fixed scroll wrap 4b under high temperature and high pressure conditions can be improved, and a highly reliable scroll compressor 50 can be obtained. it can.

<< Second Embodiment >>
Next, the scroll compressor 50 according to the second embodiment will be described with reference to FIGS. 5 and 6. FIG. 5 is a view of the orbiting scroll 3 provided in the scroll compressor 50 according to the second embodiment as seen through the end plate portion 3a of the orbiting scroll 3 (indicated by a two-dot chain line) from the lower side to the upper side of FIG. It is.

  The scroll compressor 50 according to the second embodiment is different from the scroll compressor 50 according to the first embodiment (see FIG. 1) in the configuration of the compression mechanism unit 2. That is, the scroll compressor 50 according to the first embodiment, as shown in FIG. 3, thickens the fixed scroll wrap extension 44b side of the fixed scroll wrap 4b of the fixed scroll 4 (provides a thick portion 44bt). On the other hand, as shown in FIG. 5, the scroll compressor 50 according to the second embodiment thickens the orbiting scroll wrap outer line 33a side of the orbiting scroll wrap 3b of the orbiting scroll 3 (the thick portion 33at is provided). Provided). Other points are the same as those in the first embodiment, and a description thereof will be omitted.

  As shown in FIG. 5, the orbiting scroll wrap 3b of the scroll compressor 50 according to the first embodiment has a thick portion so that the orbiting scroll wrap outer line 33a is thicker than the orbiting scroll wrap inner line 33b. 33at is provided.

In other words, from the amount of eccentricity of the eccentric portion 6b of the crankshaft 6 (the amount of eccentricity of the orbiting scroll 3), the basic thickness of the orbiting scroll wrap 3b, etc., the lap center line L ₃ (for example, the involute curve) of the orbiting scroll wrap 3b is is set, with a width equal to the inside and outside of the lap center line L _3, the basic thickness of the orbiting scroll wrap 3b is designed. The orbiting scroll wrap 3b of the scroll compressor 50 according to the second embodiment is thicker on the side of the orbiting scroll wrap outer line 33a than the basic thickness (provides a thick portion 33at). For this reason, than the width of the lap center line L ₃ to the orbiting scroll wrap extension 33b, more of the width of the lap from the center line L ₃ to the orbiting scroll wrap outside line 33a is larger.

  FIG. 6 is a partial enlarged cross-sectional view of a portion D in FIG. 1 in the scroll compressor 50 according to the second embodiment. (A) and (b) are during assembly, and (c) and (d) are during operation. Further, (a) and (c) show the side gap (side gap between the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a) of the orbiting scroll inner line side compression chamber 16a (see FIG. 2). d) shows a side gap (side gap between the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b) of the orbiting scroll outer line side compression chamber 16b (see FIG. 2). 6A to 6D, the left side is the center side of the orbiting scroll 3 and the fixed scroll 4, and the right side is the outer peripheral side of the orbiting scroll 3 and the fixed scroll 4.

As shown in FIGS. 6A and 6B, at the time of assembly, the side clearance δA ₃ formed by the orbiting scroll wrap inner line 33b and the fixed scroll wrap outer line 44a, and the orbiting scroll wrap outer line 33a and the fixed scroll are assembled. The relationship of the formula (3) is established with the side surface gap δB ₃ formed by the wrap extension line 44b.
Side gap δA ₃ > side gap δB ₃ (3)

Further, when the bearing clearance between the orbiting bearing 3c of the orbiting scroll 3 and the eccentric portion 6b of the crankshaft 6 is C, the relationship of Expression (4) is established.
Side clearance δA ₃ −side clearance δB ₃ <Bearing clearance C (4)

In other words, the side surface gap δB ₃ is smaller than the side surface gap δA ₃ by providing the thick portion 33at on the orbiting scroll wrap outer line 33a. Further, the thickness of the thick portion 33at (corresponding to “side clearance δA ₃ −side clearance δB ₃ ”) is made smaller than the bearing clearance C between the slewing bearing 3c and the eccentric portion 6b.

  On the other hand, as shown in FIGS. 6C and 6D, during operation, the end plate portion 3a is deformed by the pressure load, and the orbiting scroll wrap 3b is fixed to the fixed scroll wrap outer line 44a of the fixed scroll wrap 4b. The side gap δB between the orbiting scroll wrap outer line 33a and the fixed scroll wrap inner line 44b is enlarged.

On the other hand, the scroll compressor 50 according to the second embodiment thickens the side of the orbiting scroll wrap outer line 33a of the orbiting scroll wrap 3b (provides a thick portion 33at), thereby providing a side clearance δB during assembly. ₃ can be narrowed, and the side clearance δB ₄ during operation can also be narrowed. Thereby, the side surface gap δB ₄ can be made substantially equal to the side surface gap δA ₄ .

In other words, the side clearance .delta.B ₄ during operation, so that substantially equal to the side clearance .delta.A ₄ during operation, provided with a thick portion 33at the orbiting scroll wrap external 33a of the orbiting scroll wrap 3b. The side gaps δA ₄ and δB ₄ during operation may be the average of the side gaps, the minimum value of the side gaps, or the maximum value of the side gaps.

As described above, the scroll compressor 50 according to the second embodiment can obtain the same effect as the scroll compressor 50 according to the first embodiment by making the side surface gap δB ₄ substantially equal to the side surface gap δA _4. .

  In addition, the scroll compressor 50 according to the second embodiment can increase the rigidity of the orbiting scroll wrap 3b by increasing the wrap thickness of the orbiting scroll wrap 3b, and obtain a highly reliable scroll compressor 50. Can do.

«Third embodiment»
Next, the scroll compressor 50 according to the third embodiment will be described with reference to FIG. 7 is a view of the orbiting scroll 3 provided in the scroll compressor 50 according to the third embodiment as seen through the end plate portion 3a of the orbiting scroll 3 (shown by a two-dot chain line) from the lower side to the upper side of FIG. It is.

The scroll compressor 50 according to the third embodiment is different in the configuration of the orbiting scroll 3 from the scroll compressor 50 according to the second embodiment. That is, as shown in FIG. 5, the scroll compressor 50 according to the second embodiment makes the entire thickness of the orbiting scroll wrap outer line 33 a side of the orbiting scroll wrap 3 b of the orbiting scroll 3 (the thick portion 33 at is changed). Provided). In contrast, the scroll compressor 50 according to the third embodiment, as shown in FIG. 7, thickens the side of the orbiting scroll wrap outer line 33 a of the orbiting scroll wrap 3 b of the orbiting scroll 3 (the thick portion 33 at is provided). Provided) is different in that the range is a section from the spiral end point E ₀ of the orbiting scroll wrap outer line 33 a to the point E ₁ of approximately 180 °. The other points are the same as in the second embodiment, and the description is omitted.

As described above, the outer peripheral side of the end plate portion 3a of the orbiting scroll 3 has low rigidity because the orbiting scroll wrap 3b is less erected than the center side, and the pressure on the back pressure chamber 17 causes the center side of the end plate portion 3a. Therefore, the outer peripheral side is deformed, and the end plate portion 3a is deformed into a bowl shape (see FIG. 10). The present invention is also effective by narrowing the side surface gap δB in the section from the point E ₀ to the point E ₁ where the deformation is more likely to occur.

The thickened portion is a section from the spiral end point E ₀ to the point E _{1 of about} 180 degrees, preferably a section from the spiral end point E ₀ to the point E _{2 of about} 360 degrees. However, the present invention is effective.

<< Fourth Embodiment >>
Next, a scroll compressor 50 according to a fourth embodiment will be described with reference to FIG. FIG. 8 is a view of the fixed scroll 4 provided in the scroll compressor 50 according to the fourth embodiment when viewed from the lower side to the upper side in FIG. 1.

The scroll compressor 50 according to the fourth embodiment is different in the configuration of the fixed scroll 4 from the scroll compressor 50 according to the first embodiment. That is, as shown in FIG. 3, the scroll compressor 50 according to the first embodiment thickens the fixed scroll wrap extension 44 b side of the fixed scroll wrap 4 b of the fixed scroll 4 over the entire thickness (the thick portion 44 bt is changed). Provided). On the other hand, as shown in FIG. 8, the scroll compressor 50 according to the fourth embodiment thickens the fixed scroll wrap extension 44b side of the fixed scroll wrap 4b of the fixed scroll 4 (the thick portion 44bt is changed). Provided) is different in that the range is a section from the spiral end point F ₀ of the fixed scroll wrap extension 44 b to the point F ₁ of approximately 180 °. Other points are the same as those in the first embodiment, and a description thereof will be omitted.

Similar to the third embodiment, the present invention is also effective by narrowing the side surface gap δB in the section from the point F ₀ to the point F ₁ where the deformation is more likely to occur. The thickened portion may be a section from the spiral end point F ₀ to the point F _{1 of about} 180 degrees, preferably a section from the spiral end part F ₀ to the point F _{2 of about} 360 degrees. The present invention is effective.

≪Refrigeration equipment≫
Next, the refrigeration equipment according to the present embodiment will be described. The refrigeration equipment according to the present embodiment includes a refrigeration cycle (heat pump cycle), and includes a scroll compressor 50 according to the present embodiment (first to fourth embodiments) as a refrigerant compressor constituting the refrigeration cycle.

  Here, the refrigeration equipment is not limited to a device that supplies cold heat by a refrigeration cycle (for example, a refrigerator, a refrigeration / refrigeration showcase, an air conditioner that performs cooling operation), and supplies heat by a heat pump cycle. An apparatus (for example, a heat pump type hot water heater, an air conditioner that performs heating operation, or the like) may be used. The refrigeration equipment in the claims includes both.

  A refrigeration apparatus according to the present embodiment will be described with reference to FIG. 9, taking a heat pump hot water heater as an example. FIG. 9 is a schematic configuration diagram of a refrigeration apparatus (heat pump type hot water supply) according to the present embodiment.

  The heat pump water heater (refrigeration equipment) includes a scroll compressor 50, a first heat exchanger (condenser) 51, an expansion valve (decompression unit) 52, and a second heat exchanger (evaporator) 53. It is connected by refrigerant piping so that a working refrigerant can circulate, and a heat pump cycle is formed. Carbon dioxide refrigerant is used as the working refrigerant, and PAG (polyalkylene glycol) is used as the refrigerating machine oil (machine oil 13 (see FIG. 1)).

  The first heat exchanger (condenser) 51 includes a high-temperature and high-pressure working refrigerant discharged from the discharge pipe 1e (see FIG. 1) of the scroll compressor 50, and a heated liquid (for example, water) flowing through the liquid pipe 55. , Are to be heat exchanged. Thereby, the heat pump type hot water heater (refrigeration equipment) can heat the liquid to be heated (for example, water) flowing through the liquid pipe 55.

  The high-pressure working refrigerant radiated by the first heat exchanger (condenser) 51 is depressurized by the expansion valve (decompression means) 52 to become a low-temperature and low-pressure working refrigerant and flows into the second heat exchanger (evaporator) 53. . The second heat exchanger (evaporator) 53 exchanges heat between the low-temperature and low-pressure working refrigerant that has flowed in and the outside air. In order to promote heat exchange between the working refrigerant and the outside air, a blower fan 54 for blowing outside air to the second heat exchanger (evaporator) 53 is provided.

  The low-pressure working refrigerant that has absorbed heat by the second heat exchanger (evaporator) 53 is sucked from the suction pipe 1d (see FIG. 1) of the scroll compressor 50, and the compression mechanism section 2 (see FIG. 1 and the like) of the scroll compressor 50. ) To become a high-temperature and high-pressure working refrigerant and discharged from the discharge pipe 1e (see FIG. 1) of the scroll compressor 50.

Here, the heat pump hot water heater includes a scroll compressor 50 according to the present embodiment (first to fourth embodiments) as a compressor. When the scroll compressor 50 is in an operating state, even if the orbiting scroll 3 is pressed by the fixed scroll 4 and the end plate portion 3a of the orbiting scroll 3 is deformed as shown in FIG. The gaps (δB ₂ , δB ₄ ) with the wrap 4b can be narrowed. For this reason, the sealing property of the compression chamber 16 (refer FIG. 2) by refrigeration oil (machine oil 13 (refer FIG. 1)) can be ensured, and the leakage loss by refrigerant gas leaking from the compression chamber 16 is reduced significantly. can do. Thus, the scroll compressor 50 according to the present embodiment (first to fourth embodiments) can be a high-performance and high-reliability compressor. Therefore, the power consumption of the heat pump type hot water heater can be reduced.
≪Modification≫
In addition, the scroll compressor 50 which concerns on this embodiment (1st-4th embodiment), and refrigeration equipment provided with the same are not limited to the structure of the said embodiment, In the range which does not deviate from the meaning of invention, it is various. Can be changed.

  Although the scroll compressor 50 which concerns on this embodiment (1st-4th embodiment) demonstrated as what is a vertical scroll compressor, as shown in FIG. 1, it is not restricted to this, Horizontally placed The scroll compressor may be used, and the same effect can be obtained.

  The scroll compressor 50 according to the first and fourth embodiments is provided with a thick portion 44bt on the fixed scroll wrap inner line 44b, and the scroll compressor 50 according to the second and third embodiments is provided with a thick portion on the orbiting scroll wrap outer line 33a. Although described as providing 33at, it is not restricted to this, You may form both the fixed scroll wrap inner line 44b and the turning scroll wrap outer line 33a thickly.

  Moreover, although the carbon dioxide refrigerant was used as the working refrigerant, the present invention is not limited to this. The working refrigerant may be R410A refrigerant, R32 refrigerant, a refrigerant mixed with R32 refrigerant, R404A refrigerant, or R290 refrigerant, and the same effect is obtained. Moreover, what is necessary is just to select refrigeration oil (machine oil 13 (refer FIG. 1)) suitably according to a working refrigerant | coolant.

  Although the heat pump type hot water heater has been described as an example of the refrigeration equipment, the refrigeration equipment is not limited to this as described above. The refrigeration equipment may be a home or commercial air conditioner (air conditioner), a refrigeration machine, a refrigeration / refrigeration showcase, and the same as the example of the heat pump water heater An effect is obtained.

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Compression mechanism part 3 Orbiting scroll 3a End plate part 3b Orbiting scroll wrap 33a Orbiting scroll wrap outer line 33at Thick part 33b Orbiting scroll wrap extension 3c Orbiting bearing 4 Fixed scroll 4a End plate part 4b Fixed scroll wrap 44a Fixed scroll wrap outer line 44b Fixed scroll wrap extension 44bt Thick portion 4c Suction port 4d Discharge port 5 Frame 6 Crankshaft 7 Oldham ring 8 Motor portion 9 Lower bearing 15 Suction chamber 16 Compression chamber 16a Orbiting scroll extension side compression chamber (first compression chamber)
16b Orbiting scroll outer line side compression chamber (second compression chamber)
17 Back pressure chamber 18 Discharge pressure chamber 50 Scroll compressor 51 First heat exchanger (condenser)
52 Expansion valve (pressure reduction means)
53 Second heat exchanger (evaporator)
L ₃ orbiting scroll lap center line (orbiting lap center line)
L ₄ fixed scroll wrap center line (fixed wrap center line)
δA _{1 to} δA ₄ , δB _{1 to} δB ₄ Side clearance C Bearing clearance

Claims (6)

A turning scroll having a turning scroll wrap;
A fixed scroll having a fixed scroll wrap;
A first compression chamber formed by an inner line of the orbiting scroll wrap and an outer line of the fixed scroll wrap;
A second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap,
The side gap between the inner line of the orbiting scroll wrap and the outer line of the fixed scroll wrap, which is the side gap of the first compression chamber, is δA,
When the side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap that is the side gap of the second compression chamber is δB,
δA> δB
And,
The fixed scroll wrap is formed along a fixed wrap centerline;
The scroll compressor , wherein a width from the fixed wrap center line to the inner line of the fixed scroll wrap is larger than a width from the fixed wrap center line to the outer line of the fixed scroll wrap . A turning scroll having a turning scroll wrap;
A fixed scroll having a fixed scroll wrap;
A first compression chamber formed by an inner line of the orbiting scroll wrap and an outer line of the fixed scroll wrap;
A second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap,
The side gap between the inner line of the orbiting scroll wrap and the outer line of the fixed scroll wrap, which is the side gap of the first compression chamber, is δA,
When the side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap that is the side gap of the second compression chamber is δB,
δA> δB
And,
The orbiting scroll wrap is formed along the orbiting wrap center line,
More than the width from the turning lap center line to the inner line of the turning scroll wrap, the turning
A scroll compressor characterized in that a width from a wrap center line to an outer line of the orbiting scroll wrap is larger . A turning scroll having a turning scroll wrap;
A fixed scroll having a fixed scroll wrap;
A first compression chamber formed by an inner line of the orbiting scroll wrap and an outer line of the fixed scroll wrap;
A second compression chamber formed by an outer line of the orbiting scroll wrap and an inner line of the fixed scroll wrap,
The side gap between the inner line of the orbiting scroll wrap and the outer line of the fixed scroll wrap, which is the side gap of the first compression chamber, is δA,
When the side gap between the outer line of the orbiting scroll wrap and the inner line of the fixed scroll wrap that is the side gap of the second compression chamber is δB,
δA> δB
And,
The orbiting scroll has an orbiting bearing that fits with an eccentric part of a crankshaft,
When the bearing clearance between the slewing bearing and the eccentric portion is C,
δA−δB <C
A scroll compressor characterized by that. The scroll compressor according to any one of claims 1 to 3, wherein the side gap is a side gap during assembly. A refrigeration apparatus comprising a refrigerant circuit including the scroll compressor according to any one of claims 1 to 4 , a condenser, a decompression unit, and an evaporator. The refrigeration apparatus according to claim 5 , wherein the working refrigerant of the refrigerant circuit is carbon dioxide.

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