JP2016205153A - Scroll compressor and oldham joint for scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the strength of an Oldham joint without enlarging the Oldham joint even during a high-speed high-loading operation.SOLUTION: A scroll compressor is equipped with a fixed scroll fixed to a frame; and a swiveling scroll disposed between the fixed scroll and a frame. Both scrolls are engaged with each other, and the swiveling scroll is swivelled about the fixed scrolled while self-rotation thereof is prevented by an Oldham joint 500. The Oldham joint is equipped with a pair of first key portions 501 and 502 projecting out to the swiveling scroll side; and a pair of second key portions 504 and 505 disposed orthogonal to the first key portions and projecting out to the frame side. When a position of the first key portion is made to 0°, a cross sectional area of the Oldham joint becomes maximum at parts in which a circumferential direction position of the Oldham joint toward the swiveling direction of the swiveling scroll is 10-40° and 190-220°.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a scroll compressor used in a refrigeration air conditioner and the like, and an Oldham coupling for a scroll compressor.

  A conventional scroll compressor for refrigerating and air-conditioning is inserted into a compression mechanism portion composed of a fixed scroll, a turning scroll, a frame, etc., an electric motor including a rotor and a stator, and a hole provided in the center of the rotor. A rotating shaft that is fixed and rotated, a rolling bearing that supports the rotating shaft, a frame that supports the bearing, and a frame that is disposed between the frame and the orbiting scroll to prevent the orbiting scroll from rotating. An Oldham coupling for swiveling motion is provided in the sealed container.

  This scroll compressor forms a compression chamber between the wraps (spirals) of both scrolls by rotating the orbiting scroll with respect to the fixed scroll, and reduces the volume while moving the compression chamber to the center side. The working fluid in the compression chamber is compressed. The compressed working fluid is discharged from a discharge port provided at the center of the fixed scroll.

  An Oldham coupling as an anti-rotation mechanism for the orbiting scroll includes a key portion that engages with a key groove provided on the frame, and a key portion that engages with a key groove provided on the orbiting scroll. By sliding the groove and the key portion, the orbiting scroll is structured to be rotated while preventing rotation. Due to this operating principle, problems such as excessive load on the key part and breakage of the key part occur, especially at high speed and high pressure ratio operating conditions where the load becomes large.

  In the thing of patent 3498535 gazette (patent document 1), for the purpose of raising the intensity of a key part, without enlarging a ring width, a ring diameter, or a key width, the 1st short axis and the 1st long In an elliptical ring having an axis, the axis rotated in the counter-rotating direction of the shaft from the first minor axis is the second minor axis, the axis orthogonal to the second minor axis is the second major axis, An elliptical ring composed of two minor axes and a second major axis is provided with a key that makes an opposing pair from the elliptical ring located on the first minor axis, and further on the first major axis. A key having a pair of opposing keys from an elliptical ring located at the center is proposed.

  According to this patent document 1, the key bending moment can be reduced by reducing the length of the arm from the stress concentration point at the base of the key portion on the surface receiving the load of each key. To alleviate the stress concentration at the base of the key part and increase the strength of the key part without increasing the ring width, ring diameter, or key width, thereby reducing the size of the Oldham coupling and reducing the size of the scroll compressor as a whole Is described.

Japanese Patent No. 3498535

  By the way, recent scroll compressors are required to be further reduced in size and speed. When the speed is increased, the inertial force when the orbiting scroll makes an orbiting motion increases, and the load applied to the key portion on the orbiting scroll side increases. Therefore, the stress generated in the Oldham joint also increases and the risk of damage to the Oldham joint increases. In the thing of the said patent document 1, sufficient consideration is not made regarding ensuring sufficient intensity | strength, without enlarging an Oldham coupling even at the time of the high-speed high load operation of a scroll compressor.

  An object of the present invention is to obtain a scroll compressor and an Oldham joint for a scroll compressor, which can improve the strength without increasing the size of the Oldham joint even during high-speed and high-load operation.

  In order to achieve the above object, the present invention includes a fixed scroll fixed to a frame, and a turning scroll disposed between the fixed scroll and the frame, and meshes the scrolls, and the turning scroll. Is a scroll compressor configured to orbit with respect to the fixed scroll while preventing rotation by an Oldham joint, wherein the Oldham joint includes a pair of first key portions projecting toward the orbiting scroll. And a pair of second key portions arranged so as to be orthogonal to the first key portion and projecting to the frame side, and when the position of the first key portion is 0 °, the turning of the orbiting scroll The cross-sectional area of the Oldham joint is maximized when the circumferential position of the Oldham joint is 10 to 40 ° and 190 to 220 °. Characterized in that it is configured so that.

  Another feature of the present invention is an Oldham coupling for a scroll compressor configured to cause the orbiting scroll to orbit with respect to the fixed scroll while preventing its rotation, and a pair of first protrusions protruding toward the orbiting scroll. And a pair of second key portions that are arranged to be orthogonal to the first key portion and project to the frame side, and when the position of the first key portion is 0 °, A scroll compressor configured so that the cross-sectional area of the Oldham joint is maximized in a portion where the circumferential direction position of the Oldham joint is 10 to 40 ° and a portion of 190 to 220 ° toward the turning direction of the orbiting scroll. For Oldham fittings.

  ADVANTAGE OF THE INVENTION According to this invention, there exists an effect which can obtain the scroll compressor which can improve the intensity | strength, without enlarging an Oldham coupling, and the Oldham coupling for scroll compressors also at the time of a high-speed high load operation.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention. The top view of the flame | frame shown in FIG. The bottom view of the turning scroll shown in FIG. The bottom view of the Oldham coupling explaining the example currently generally used regarding the Oldham coupling shown in FIG. The diagram which shows the change of the maximum principal stress in the circumferential direction angular position of the Oldham coupling shown in FIG. The bottom view explaining the structure of the Oldham coupling in Example 1 of this invention.

  Hereinafter, specific examples of the scroll compressor and the Oldham coupling for the scroll compressor according to the present invention will be described with reference to the drawings. In each figure, the part which attached | subjected the same code | symbol has shown the part which is the same or it corresponds.

Hereinafter, Example 1 of the scroll compressor and Oldham coupling for scroll compressor of the present invention will be described with reference to FIGS.
First, the whole structure of a scroll compressor is demonstrated using FIGS. 1-3.
1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention, FIG. 2 is a plan view of a frame shown in FIG. 1, and FIG. 3 is a bottom view of the orbiting scroll shown in FIG.

The scroll compressor 1 of the first embodiment shown in FIG. 1 is a scroll compressor for refrigeration air conditioning, and the working fluid is a refrigerant gas flowing through the refrigeration cycle.
The scroll compressor 1 houses a compression mechanism portion 2 that compresses a working fluid (refrigerant gas) and a drive portion 3 that drives the compression mechanism portion 2 via a rotary shaft 300 in a cylindrical sealed container 700. Configured. In the present embodiment, as a vertical scroll compressor in which the compression mechanism 2 and the drive unit 3 are disposed in the sealed container 700 in order from the top, and an oil sump 730 is formed in the lower part of the drive unit 3. Yes.

  The sealed container 700 has an upper cap 710 and a lower cap 720, and the upper cap 710 and the lower cap 720 are fitted so as to cover the central cylindrical portion of the sealed container 700 on the outside. The part is heated and welded by the welding torch from obliquely downward and obliquely upward. Legs 721 are attached to the bottom surface of the sealed container 700. A magnet 722 is attached to the inner side of the lower cap 720, and plays a role of collecting dust in the compressor.

  A hermetic terminal 702 and a terminal cover 703 are provided on the side surface of the hermetic container 700 so that electric power can be supplied to the electric motor 600 constituting the driving unit 3. The Hermetic terminal 702 is provided through the sealed container 700 and is disposed between the coil end 601a of the stator 601 constituting the electric motor 600 and the frame 400 constituting the compression mechanism unit 2. Yes.

The compression mechanism unit 2 includes a fixed scroll 100, a turning scroll 200, and the frame 400 as basic elements.
The fixed scroll 100 includes a base plate 101, a wrap (scroll wrap) 102 which is a spiral body provided vertically below the base plate 101, and a suction port 103 provided on the outer peripheral side of the base plate 101. And a discharge port 104 provided on the center side of the base plate. The fixed scroll 100 is fixed to the frame 400 by a plurality of bolts 405 that are equally arranged in the circumferential direction.

  The orbiting scroll 200 is formed so as to protrude perpendicularly to a base plate 201, a wrap (scroll wrap) 202 standing vertically on the upper side of the base plate 201, and a back side (anti-wrap side) of the orbiting scroll. The swivel boss portion 203, a swivel bearing (slide bearing) 210 that is press-fitted into the swivel boss portion 203, and a back pressure hole (not shown) formed in the base plate 201. Yes. The orbiting scroll 200 is formed by processing each component from a casting made of cast iron or aluminum.

  The orbiting scroll 200 is disposed between the fixed scroll 100 and the frame 400, and the fixed scroll 100 and the orbiting scroll 200 mesh with each other with the wraps 102 and 202 facing inward. Further, the base plate 201 of the orbiting scroll 200 is provided so as to be sandwiched between the fixed scroll 100 and a base 430 (see FIG. 2) of the frame 400. An Oldham joint (spinning prevention mechanism) 500 is provided between the rear surface of the orbiting scroll 200 and the frame 400 for preventing the orbiting scroll 200 from rotating and causing orbiting motion. The orbiting scroll 200 is orbitally driven by the driving unit 3.

  The drive unit 3 includes an electric motor 600 including a stator 601 and a rotor 602, a rotating shaft 300 that is inserted and fixed at the center of the rotor 602, and rotates integrally with the rotor 602. An oil supply pump 900 for sucking up oil in the oil reservoir 730 is press-fitted to the lower end of the rotary shaft 300.

  The rotating shaft 300 is formed eccentrically on the upper end side thereof, and is inserted into the orbiting bearing 210 on the back side of the orbiting scroll 200, the main shaft portion 302 on the lower side, and the auxiliary bearing support on the lower end side. The unit 303 is configured. The main shaft portion 302 and the auxiliary bearing support portion 303 are formed on the same axis and constitute a main shaft portion. The upper end side (the upper side of the electric motor) of the main shaft portion 302 is supported by a main bearing 401 provided on the frame 400, and the auxiliary bearing support portion 303 is a lower frame fixed to the hermetic container 700 below the electric motor 600. 801 is supported by a secondary bearing 803 provided via a secondary bearing housing 802.

  The main bearing 401 and the sub-bearing 803 are constituted by rolling bearings, and constitute a rotating shaft support portion that rotatably supports the rotating shaft 300. The crank pin 301 is engaged with the slewing bearing 210 by being movable in the axial direction (thrust direction) and rotatably.

  The auxiliary bearing housing 802 is fixed to the lower frame 801 with bolts 805. The auxiliary bearing 803 is inserted into the auxiliary bearing housing 802 from above, and a housing cover 804 is attached above the auxiliary bearing 803.

  The oil supply pump 900 is a centrifugal pump attached to the lower end of the rotary shaft 300, forcibly sucks the lubricating oil stored in the oil sump 730 through the oil supply hole 901, and axially enters the rotary shaft 300. Through the formed oil passage 311, the auxiliary bearing 803, the swing bearing 210 and the main bearing 401 are supplied. Further, the oil supplied from the oil passage 311 is also supplied to the sliding portion between the fixed scroll 100 and the orbiting scroll 200.

  The oil passage 311 is provided so as to penetrate the rotary shaft 300 in the axial direction, and a lower oil supply hole concentric with the axis of the rotary shaft 300 and an upper oil supply eccentric with respect to the axis of the rotary shaft 300. And a hole. The auxiliary bearing 803 is supplied with oil through a lateral hole 312 communicating with the lower oil supply hole.

  The frame 400 is fixed to the inner peripheral surface of the sealed container 700 at a plurality of locations in the circumferential direction by welding 740. The frame 400 includes a bearing support portion 401a that supports the main bearing 401, and a compression mechanism support portion 401b that extends outward from an upper portion of the bearing support portion 401a and supports the compression mechanism portion 2. The entire lower surface of the compression mechanism support 401b is formed flat and is positioned above the discharge pipe 701. The discharge pipe 701 is for discharging the refrigerant gas compressed by the compression mechanism unit 2 to the refrigeration cycle, and is provided to penetrate the sealed container 700 at the top of the electric motor 600.

  As shown in FIG. 2, the frame 400 is slid by engaging with the base 430 for the orbiting scroll 200 and a pair of key portions 504 and 505 (see FIG. 4) of the Oldham joint 500. A stationary base 432 is provided that forms a pair of key grooves 431a and 431b. The pair of key grooves 431 a and 431 b formed in the stationary base 432 are arranged so as to linearly move the Oldham joint 500 from side to side with respect to the frame 400.

  In FIG. 2, 700 is the sealed container 700 shown in FIG. 1, and 410 shown in FIGS. 1 and 2 is a seal ring groove in which the seal ring 410a is accommodated. Further, the frame 400 forms a back pressure chamber 411 between the back side of the orbiting scroll 200 and the fixed scroll 100 in order to give an appropriate pressing force (back pressure) to the orbiting scroll 200. . That is, the back pressure chamber 411 is a space formed by being surrounded by the orbiting scroll 200, the frame 400, and the fixed scroll 100.

  In FIG. 1, reference numeral 130 denotes a compression chamber formed by engaging a scroll wrap 102 of the fixed scroll 100 and a wrap 202 of the orbiting scroll 200. The back plate 201 of the orbiting scroll 200 is provided with a back pressure hole (not shown) that allows the compression chamber 130 and the back pressure chamber 411 on the back of the orbiting scroll base plate 201 to communicate with each other. The pressure of 411 is maintained at an intermediate pressure (intermediate pressure) between the suction pressure and the discharge pressure.

  A seal ring 410 a is provided in the seal ring groove 410 formed on the upper surface of the frame 400, and the seal ring 410 a prevents compressed gas from flowing into the back pressure chamber 411. That is, as shown in FIG. 3, a plurality of oil supply pockets 205 are provided in the circumferential direction on the lower end surface of the orbiting boss portion 203 of the orbiting scroll 200. The pocket 205 reciprocates between the outer side and the inner side of the seal ring 410 a and conveys a part of the oil between the swivel bearing 210 and the main bearing 401 to the back pressure chamber 411. The conveyed oil is supplied to the Oldham coupling 500 and then supplied to the end face 105 of the fixed scroll and the sliding face of the base plate 201 of the orbiting scroll 200.

The orbiting scroll 200 is pressed against the fixed scroll 100 by the resultant force of the intermediate pressure of the back pressure chamber 411 and the discharge pressure acting on the inside of the seal ring 410a.
In the orbiting scroll 200 shown in FIG. 3, reference numeral 210 denotes the orbiting bearing that is press-fitted into the inner surface of the orbiting boss 203. A pair of key portions 501 and 502 (see FIG. 4) formed on the orbiting scroll side of the Oldham coupling 500 are engaged and slid in the pair of key grooves 221a and 221b.

  The inner diameter of the seal ring 410a is smaller than the outer diameter of the main bearing 401. In order to be able to adopt such a configuration, the main bearing 401 is moved from the drive unit 3 side of the frame 400 to the frame 400. The rolling bearing 401 is fixed by a frame cover 403. A thrust bearing 402 is provided on the frame cover 403. The frame cover 403 is manufactured separately from the frame 400 and is fixed to the frame 400 with bolts 406. By fixing the bolts in this way, the gap between the frame cover 403 and the frame 400 can be sealed, and oil leakage from the oil supply path can be suppressed. The frame cover 403 includes a portion that is inserted inside the frame 400 and presses the main bearing 401, and a portion that contacts and is fixed to the end surface of the frame 400 on the driving unit 3 side. Yes.

  407 shown in FIG. 1 is a balance weight, and this balance weight 407 is fixed to the rotating shaft 300 so as to be positioned closer to the motor side than the main bearing 401. In this embodiment, the balance weight 407 is formed separately from the rotary shaft 300 and is press-fitted and fixed to the rotary shaft 300. However, the balance weight 407 is the rotary shaft. 300 may be formed integrally. The maximum outer diameter portion of the balance weight 407 is provided so as to protrude from the end face side of the coil end 601a of the stator 601 and is configured to have a larger diameter than the inner diameter of the coil end 601a. Thereby, a sufficient rotation balance of the rotating shaft 300 can be ensured.

  In FIG. 1, 408 is an oil drain pipe for returning the lubricating oil supplied to the main bearing 401 to the oil reservoir 730, and 711 introduces refrigerant gas from the refrigeration cycle to the inlet 103 of the fixed scroll 100. This is an intake pipe.

Next, the operation of the scroll compressor will be described.
When the crank pin 301 rotates eccentrically due to the rotation of the rotary shaft 300 connected to the rotor 602 of the electric motor 600, the compression mechanism unit 2 does not rotate with respect to the fixed scroll 100 by the Oldham joint 500. Make a swivel motion. Accordingly, the refrigerant gas as the working gas is introduced into the compression chamber 130 formed by the wraps 102 and 202 through the suction pipe 711 and the suction port 103. The compression chamber 130 is compressed by the refrigerant gas as the volume of the compression chamber 130 decreases while moving toward the center by the orbiting motion of the orbiting scroll 200.

The compressed refrigerant gas is discharged into the sealed container 700 from a discharge port 104 provided at the center of the fixed scroll 100. Thereafter, the discharged refrigerant gas is formed between the frame 400 and the sealed container 700. It flows to the drive unit 3 side through a formed passage (not shown). As a result, the space in the sealed container 700 is maintained at the discharge pressure, and the discharged refrigerant gas circulates around the compression mechanism 2 and the electric motor 600 and then enters the refrigeration cycle outside the sealed container 700 from the discharge pipe 701. Released.
In addition, as refrigerant gas compressed by the said compression mechanism part 2, refrigerant | coolants, such as R410A friendly to a global environment, are used.

Next, an oil supply path in the scroll compressor 1 described above will be described.
When the rotating shaft 300 is rotated, the oil in the oil reservoir 730 is boosted and supplied to the oil passage 311 formed in the rotating shaft 300 by the oil supply pump 900. Part of the oil sent to the oil passage 311 flows to the auxiliary bearing 803 through the lateral hole 312 and then returns to the oil reservoir 730. The oil that has reached the upper portion of the crankpin 301 through the oil passage 311 flows to the main bearing 401 after lubricating the slewing bearing 210. Most of the oil that has lubricated the main bearing 401 passes through the oil drain pipe 408 and returns to the oil sump 730.

  Since the refueling pocket 205 is provided on the end face of the revolving boss portion 203 of the orbiting scroll 200, the revolving scroll 200 revolves so that the refueling pocket 205 straddles the seal ring 410a and the seal ring 410a Go back and forth between outside and inside. As a result, part of the oil between the slewing bearing 210 and the main bearing 401 is conveyed to the back pressure chamber 411 through the oil supply pocket 205. After the oil conveyed to the back pressure chamber 411 lubricates the Oldham coupling 500, a part of the oil is supplied to the sliding surface between the end plate surface 105 of the fixed scroll 100 and the base plate 201 of the orbiting scroll 200, It flows into the compression chamber 130 through a minute gap on the sliding surface. Further, the oil conveyed to the back pressure chamber 411 flows into the compression chamber 130 through a back pressure hole (not shown). The oil flowing into the compression chamber 130 is discharged from the discharge port 104 together with the compressed refrigerant gas, separated from the refrigerant gas in the sealed container 700, and returned to the oil reservoir 730.

  Next, with respect to the Oldham joint 500 shown in FIG. 1, first, an example of an Oldham joint that is currently used generally will be described with reference to FIG. FIG. 4 is a bottom view of an Oldham joint that is currently generally used.

  As shown in FIG. 4, Oldham coupling 500 includes a ring portion 503, a pair of first key portions (orbiting scroll side key portions) 501 and 502 formed on the orbiting scroll side of the ring portion 503, and the ring. A pair of second key portions (frame side key portions) 504 and 505 formed on the frame side of the portion 503 are provided. The first key parts 501 and 502 engage and slide with key grooves 221a and 221b (see FIG. 3) formed on the base plate 201 of the orbiting scroll 200, and the second key parts 503 and 504 are engaged. Engages and slides in key grooves 431a and 431b (see FIG. 2) formed in the stationary base 432 of the frame 400.

  The operation of the Oldham coupling 500 will be described. A pair of first key portions 501 and 502 out of first and second pair of key portions formed orthogonal to the Oldham joint 500 engage with the key grooves 221a and 221b of the orbiting scroll 200 and slide. The other pair of second key portions 504 and 505 engage with and slide on the key grooves 431a and 431b of the frame 400 which is the receiving portion of the Oldham coupling 500. As a result, the orbiting scroll 200 can orbit within the plane perpendicular to the axial direction, which is the direction in which the scroll wrap 202 stands, without rotating with respect to the fixed scroll 100.

Next, the stress generated in Oldham coupling 500 shown in FIG. 4 will be examined.
A load acting on the first key portions 501 and 502 on the orbiting scroll side is Fs, and a load acting on the second key portions 504 and 505 on the frame side is Ff. Further, the Oldham key portion load generated by the gas load during the compression operation of the scroll compressor is F1, and the Oldham key portion load generated by the inertial force due to the orbiting scroll 200 is revolving is F2.

  The Oldham key portion load generated by the gas load F1 and the Oldham key portion load generated by the inertial force F2 can be obtained by the following equations (1) and (2).

F1 = 1/2 × K × J / (R / 2) (1)
F2 = 1/4 × M × ε × ω ² × sin θ (2)
Here, K is a load coefficient, a coefficient for correcting a deviation from an actually applied load, J is a turning autorotation moment (kg · m), a moment generated when the turning scroll makes a turning motion, and R is Oldham. The average diameter (m) of the joint, ε is the turning radius (m), M is the Oldham ring mass (kg), ω is the angular velocity (rad / s), and θ is the rotation angle (°) of the turning scroll.

  Only the load F1 due to the gas load acts on the second key portion (frame side key portion), whereas the load F1 due to the gas load acts on the first key portion (orbiting scroll side key portion). In addition, the load F2 generated by the inertial force caused by the orbiting scroll 200 is also acted. That is, the load Fs acting on the first key portions 501 and 502 and the load Ff acting on the second key portions 504 and 505 can be obtained by the following equations (3) and (4).

Fs = F1 + F2 (3)
Ff = F1 (4)
For this reason, as the rotation speed of the scroll compressor increases, the influence of the inertial force generated by the orbiting motion of the orbiting scroll 200 increases, and the load acting on the first key portions 501 and 502 increases. It is expected that the stress generated in the ring part 503 in the vicinity of the key part also increases.

  Therefore, in the Oldham coupling 500 shown in FIG. 4, the maximum principal stress generated at each circumferential angular position in the ring portion 503 was analyzed. The result is shown in FIG. FIG. 5 is a diagram showing a change in maximum principal stress at an angular position in the circumferential direction of the Oldham joint shown in FIG.

  The stress analysis condition of FIG. 5 is that the load is applied to the second key portions 504 and 505 on the frame side as a result of the load being applied to the first key portions 501 and 502 on the orbiting scroll side during the operation of the scroll compressor. Therefore, the analysis is performed under the condition that a load is applied to the first key portions 501 and 502.

  That is, a load is applied to each of the first key portions 501 and 502 on the orbiting scroll side, and the applied load is converted into a surface pressure. The second key portions 504 and 505 on the frame side and the central axis are side-constrained. At this time, it is assumed that the inner cylindrical portion is also filled with a material having a Young's modulus of 1 kPa and a Poisson's ratio of 0.45. For the load applied to the first key portions 501 and 502, for example, the load Fs calculated based on the above-described equations (1) to (4) is used.

  FIG. 5 is a diagram obtained by analyzing and extracting the stress distribution in the cross section at each circumferential angular position of the Oldham joint 500 under such conditions and extracting the maximum value (maximum principal stress). The angle of the horizontal axis in FIG. 5 corresponds to the angle shown in FIG. 4, the first key portion 501 is 0 ° (or 360 °), and the second key portion 504 is 90 °. The position of the first key portion 502 is 180 °, and the position of the second key portion 505 is 270 °.

  As shown in FIG. 5, the maximum principal stress of the Oldham coupling 500 that is currently used generally has a maximum value in the vicinity of the first key portions (orbiting scroll side key portions) 501 and 502, It has been found that there is a minimum value in the vicinity of the second key portions (frame side key portions) 504 and 505.

  That is, when the position of the first key portion 501 is set to 0 °, the Oldham joint 500 has a circumferential position of 10 to 40 ° toward the turning direction of the orbiting scroll 200 (the rotation direction of the rotary shaft). And the value of the maximum principal stress in the portion of 190 to 220 ° is the largest. Moreover, it turned out that the value of the maximum principal stress is the smallest at the 80-120 degree part and the 260-300 degree part of the circumferential position of the Oldham joint toward the turning direction of the turning scroll 200. .

  Therefore, the scroll compressor of this embodiment is configured as shown in FIG. FIG. 6 is a bottom view for explaining the configuration of the Oldham coupling in Example 1 of the present invention. In FIG. 6, d1 indicates the inner diameter portion of the Oldham coupling in the present embodiment, and d2 indicated by a two-dot chain line indicates the inner diameter portion of the general Oldham coupling shown in FIG. 4 for reference. .

  The scroll compressor in the present embodiment is the same as that described with reference to FIGS. Also, the Oldham joint 500 is basically the same as the Oldham joint shown in FIG. 4, and a pair of first key portions 501, 502 projecting toward the orbiting scroll 200, and the first key portion 501, A pair of second key portions 504 and 505 are provided so as to be orthogonal to 502 and project to the frame side.

  However, according to the Oldham coupling 500 in this embodiment, the cross-sectional area of the ring portion 503 in the vicinity of the first key portions 501 and 502 is based on the analysis result of FIG. The cross-sectional area of the ring portion 503 in the vicinity of 504 and 505 is larger.

  Further details will be described. In general, since the relationship of “stress = load / cross-sectional area” is established, the stress generated in the Oldham joint 500 can be reduced by increasing the cross-sectional area of the ring portion 503 of the Oldham joint 500. Therefore, based on the analysis result of FIG. 5, in this embodiment, as shown in FIG. 6, when the position of the first key portion 501 in the Oldham coupling 500 is 0 °, the turning direction of the orbiting scroll is set. The circumferential position of the Oldham joint 500 is configured so that the cross-sectional area of the Oldham joint 500 is maximized at a portion of 10 ° to 40 ° and a portion of 190 ° to 220 ° toward the rotation direction of the rotating shaft. It is what you are doing.

  That is, the circumferential position of the Oldham joint 500 is configured such that the inner diameter of the Oldham joint at the portion of 10 to 40 ° and the portion of 190 to 220 ° is smaller than the inner diameter of the Oldham joint at other circumferential positions. It is set as the structure which expands the cross-sectional area of the said 10-40 degree part of an Oldham coupling, and the said 190-220 degree part.

  Further, in this embodiment, as shown in FIG. 6, when the position of the first key portion is 0 °, the circumferential position of the Oldham joint is 80 to 120 ° toward the turning direction of the orbiting scroll. And the cross-sectional area of the Oldham joint at 260 to 300 [deg.].

  That is, the circumferential position of the Oldham joint 500 is configured so that the inner diameter of the Oldham joint at the portion of 80 to 120 ° and the portion of 260 to 300 ° is larger than the inner diameter of the Oldham joint at other circumferential positions. The cross-sectional area of the 80-120 ° portion and the 260-300 ° portion of the Oldham joint is minimized.

  With this configuration, it is possible to suppress an excessive stress from being generated in the ring portion 503 due to a load acting on the first key portions 501 and 502 of the Oldham joint 500, and during high-speed and high-load operation. Even if it exists, the scroll compressor which can fully improve intensity | strength, without enlarging an Oldham coupling is obtained.

  Furthermore, in this embodiment, as shown in FIG. 6, from the ring portion in the vicinity of the first key portions 501 and 502 of the Oldham joint 500 to the ring portion in the vicinity of the second key portions 504 and 505, The cross-sectional area is continuously changed.

  That is, from the portion where the circumferential position of the Oldham joint 500 described above is 80 to 120 ° (the portion where the cross-sectional area is minimum) to the portion where 190 to 220 ° (the portion where the cross-sectional area is maximum), and the Oldham joint. The inner diameter of the Oldham joint is continuously increased from a portion of 260 to 300 ° (a portion where the cross-sectional area is minimum) to a portion of 10 to 40 ° (a portion where the cross-sectional area is maximum). The cross-sectional area of the ring portion is configured to continuously increase so as to decrease.

  Further, the position in the circumferential direction of the Oldham joint extends from a portion of 10 to 40 ° (a portion where the cross-sectional area is maximum) to a portion of 80 to 120 ° (a portion where the cross-sectional area is minimum), and the circumference of the Oldham joint. The inner diameter of the Oldham joint is continuously increased from the 190-220 ° portion (where the cross-sectional area is maximized) to the 260-300 ° portion (where the cross-sectional area is minimum). Thus, the cross-sectional area of the ring portion is configured to continuously decrease.

  Thus, in this embodiment, the ring section sectional area is continuously increased from the portion where the sectional area of the Oldham joint 500 is minimized to the portion where the sectional area is maximized, and the sectional area is maximized. The ring cross-sectional area is continuously reduced from the part to the part where the cross-sectional area is minimized. That is, the cross-sectional area gradually changes by making the inner diameter side diameter of the ring portion 503 gradually smaller or larger toward the center of the Oldham joint 500. It is possible to further improve the strength of the Oldham joint by avoiding stress concentration due to the change of.

  Further, from the analysis results shown in FIG. 5, the stress change widths in the ranges of 0 ° to 90 ° and 180 ° to 270 ° are large, whereas the stress change widths in the ranges of 90 ° to 180 ° and 270 ° to 360 °. Is small.

  Therefore, in this embodiment, the cross-sectional area of the ring portion 503 is enlarged or reduced so as to improve the distribution of stress generated in the Oldham joint 500. In consideration of the fact that the stress is inversely proportional to the cross-sectional area, in this embodiment, each cross-sectional area of the ring portion 503 of the Oldham joint 500 is obtained by the following relational expression (5), and the change in the maximum principal stress shown in FIG. Correspondingly, the ring section cross-sectional area is continuously changed.

Cross-sectional area after improvement = cross-sectional area before improvement x (stress value of current product / stress value after improvement) (5)
In addition, when the cross-sectional area calculated by Expression (5) is used, the shape may be uneven, and in order to avoid stress concentration due thereto, in this embodiment, the inner diameter side in each circumferential part of the ring portion 503 is expressed by the above expression. The elliptical shape is approximately matched to the improved cross-sectional area obtained in (5). Further, this elliptical shape has a shape as shown in FIG. 6 corresponding to the stress change width of each region shown in FIG. By comprising in this way, it becomes possible to further reduce the stress which generate | occur | produces in Oldham coupling 500.

  Furthermore, in this embodiment, the Oldham joint 500 is manufactured by a casting forging method. By manufacturing the Oldham joint 500 by a casting forging method, it becomes possible to make the shape close to the final shape as compared with the one manufactured by an extruded material or the like. As a result, it is possible to manufacture the Oldham joint 500 by machining only the minimum necessary area, such as the sliding surface of the Oldham joint, which requires high surface accuracy, and the manufacturing process is reduced and manufactured at low cost. it can.

  As described above, according to the scroll compressor of this embodiment, when the position of the first key portion is 0 °, the circumferential position of the Oldham joint is 10 toward the turning direction of the orbiting scroll. Since the cross-sectional area of the Oldham joint is maximized at a portion of ˜40 ° and a portion of 190˜220 °, the Oldham joint is not enlarged even during high-speed and high-load operation. A scroll compressor capable of improving the strength can be obtained. Therefore, the Oldham coupling can be prevented from being damaged at high speed and high load and reliability can be ensured without increasing the size of the scroll compressor used in the refrigeration air conditioner or the like.

  In addition, this invention is not limited to the Example mentioned above, Various modifications are included. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1: scroll compressor, 2: compression mechanism unit, 3: drive unit,
100: fixed scroll, 101: base plate, 102: wrap, 103: suction port,
104: Discharge port, 105: End plate surface, 130: Compression chamber,
200: Orbiting scroll 201: Base plate 202: Lap
203: Rotating boss part, 205: Refueling pocket,
221a, 221b: keyway for orbiting scroll, 210: orbiting bearing (slide bearing),
300: Rotating shaft 301: Crank pin 302: Main shaft portion 303: Sub-bearing support portion
311: Oil passage, 312: Side hole,
400: frame,
401: Rolling bearing (main bearing), 401a: Bearing support, 401b: Compression mechanism support,
402: Thrust bearing, 403: Frame cover, 405, 406, 805: Bolt,
407: Balance weight, 408: Oil drain pipe,
410: seal ring groove, 410a: seal ring,
411: Back pressure chamber, 430: Base, 432: Stationary base,
431a, 431b: keyway of the frame,
500: Oldham coupling,
501, 502: first key part (orbiting scroll side key part),
503: Ring part,
504, 505: second key part (frame side key part),
600: Electric motor, 601: Stator, 601a: Coil end, 602: Rotor,
700: Airtight container, 701: Discharge pipe, 702: Hermetic terminal, 703: Terminal cover,
710: upper cap, 711: suction pipe, 720: lower cap, 721: leg,
722: Magnet, 730: Oil sump, 740: Welded part,
801: Lower frame, 802: Sub bearing housing, 803: Rolling bearing (sub bearing),
804: Housing cover, 900: Pump part, 901: Oil supply hole.

Claims (8)

A fixed scroll fixed to the frame; and a turning scroll disposed between the fixed scroll and the frame; and engaging both the scrolls, while preventing the rotation of the turning scroll by an Oldham coupling. A scroll compressor configured to swivel with respect to a fixed scroll,
The Oldham coupling includes a pair of first key portions protruding to the orbiting scroll side, and a pair of second key portions arranged to be orthogonal to the first key portion and protruding to the frame side,
When the position of the first key portion is 0 °, the Oldham joint is located at a portion in which the circumferential direction of the Oldham joint is 10 to 40 ° and 190 to 220 ° in the turning direction of the orbiting scroll. A scroll compressor characterized in that the cross-sectional area is maximized. The scroll compressor according to claim 1, wherein
When the position of the first key portion is set to 0 °, the Oldham joint is located at a portion where the circumferential direction position of the Oldham joint is 80 to 120 ° and 260 to 300 ° toward the turning direction of the orbiting scroll. A scroll compressor characterized in that the cross-sectional area is minimized. The scroll compressor according to claim 2,
From the portion where the cross-sectional area of the Oldham joint is minimized to the portion where the cross-sectional area is maximum, the cross-sectional area of the ring portion is continuously increased, and the cross-sectional area of the Oldham joint is maximized. A scroll compressor characterized in that the cross-sectional area of the ring portion is continuously reduced from the portion to the portion where the cross-sectional area is minimized. The scroll compressor according to claim 1, wherein
By configuring the Oldham joint with an inner diameter smaller than the inner diameter of the Oldham joint at other circumferential positions, the Oldham joint has a circumferential position of 10 to 40 ° and a 190 to 220 ° portion. The scroll compressor characterized by expanding the cross-sectional area of the said 10-40 degree part and the said 190-220 degree part from the cross-sectional area in another circumferential direction position. The scroll compressor according to claim 1, wherein
Until the circumferential position of the Oldham joint reaches from 80 to 120 ° to 190 to 220 °, and until the circumferential position of the Oldham joint reaches from 260 to 300 ° to 10 to 40 ° The scroll compressor is characterized in that the inner diameter of the Oldham coupling is continuously reduced, and the cross-sectional area of the ring portion is continuously increased. The scroll compressor according to claim 5, wherein
Until the circumferential position of the Oldham joint reaches from 10 to 40 ° to 80 to 120 °, and until the circumferential position of the Oldham joint reaches from 190 to 220 ° to 260 to 300 ° The scroll compressor is characterized in that the inner diameter of the Oldham coupling is continuously increased so that the cross-sectional area of the ring portion is continuously reduced.   2. The scroll compressor according to claim 1, wherein an Oldham joint manufactured by a casting forging method is used as the Oldham joint. An Oldham coupling for a scroll compressor configured to cause the orbiting scroll to orbit with respect to the fixed scroll while preventing rotation.
A pair of first key portions protruding to the orbiting scroll side, and a pair of second key portions arranged to be orthogonal to the first key portion and protruding to the frame side,
When the position of the first key portion is 0 °, the Oldham joint is located at a portion in which the circumferential direction of the Oldham joint is 10 to 40 ° and 190 to 220 ° in the turning direction of the orbiting scroll. An Oldham coupling for a scroll compressor, characterized in that the cross-sectional area of the scroll compressor is maximized.

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