JPH0526186A - Scroll compressor - Google Patents

Abstract

PURPOSE:To prevent the performance lowering of a compressor due to strong contact between laps caused by deformation during operation and the generation of abnormal wear at sliding parts in this scroll compressor used as a refrigerant compressor for refrigerating air-conditioning, a refrigerator, or the like. CONSTITUTION:Surface hardening is applied to the thrust sliding face of the end plate outer peripheral part of a turning scroll. Fittness layers 32 are provided at a lap part and an end plate part 6a, and the thickness of the fittness layer 32 on the thrust sliding face of the end plate outer peripheral part is set smaller than that on the lap part side. In a scroll compressor with a lightweight aluminum alloy used for the turning scroll and with cast iron used for a fixed scroll, the lap height is set into such tapered shape that the lap center part height on the turning side is lower by scores of mu than the outer peripheral lap part height, and the fittness layers 32 are uniformly attached to the end plate part 6a and lap part of the turning scroll 6.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used as a refrigerant compressor for refrigeration and air conditioning, refrigerators and the like.

[0002]

2. Description of the Related Art A scroll compressor is disclosed in JP-A-54-157315.
The publication discloses a structure of a compressor in which the entire surface of the scroll wrap portion and the end plate portion is made of a material that easily wears to easily reduce the gap between the scrolls.

[0003]

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention
In 157315, although the entire surface of the wrap portion and the end plate portion of the scroll is made of a material that easily wears, the structure does not consider thermal deformation or pressure deformation during operation of the scroll member. An example of the prior art is shown in FIG. FIG. 13 is a scroll meshing pattern in a state in which the entire surface of the scroll wrap portion and the end plate portion is made of a material that easily wears. In this way, in reality, the amount of wear of the substance that easily wears due to deformation greatly differs between the central portion and the outer peripheral portion of the scroll wrap portion or the end plate portion. Therefore, in some cases, abrasion may be promoted even to the background of the base material. In particular, in the case of a scroll compressor consisting of a scroll combination that uses a lightweight aluminum alloy for the orbiting scroll and a cast iron material for the fixed scroll, the amount of wear in each part due to the degree of deformation The difference becomes noticeable. In such a conventional technique, the gap adjusting function between the scrolls becomes insufficient, and a problem occurs that a strong lap hits and the gap between the laps becomes large, resulting in performance deterioration and abnormal increase in wear amount.

[0004]

According to the present invention, a surface hardening treatment is applied to the thrust sliding surface of the outer peripheral portion of the end plate of an orbiting scroll, and a familiar layer is attached to the wrap portion and the end plate portion of the orbiting scroll to form the outer periphery of the end plate. The thickness of the familiar layer on the thrust sliding surface of the section is set smaller than the thickness of the familiar layer on the lap side.
Alternatively, a wear-resistant plate is incorporated in the thrust sliding surface of the end plate of the orbiting scroll, and a familiar layer is attached to the surface of the wear-resistant plate. In a scroll compressor that uses a scroll combination that uses a lightweight aluminum alloy for the orbiting scroll and a cast iron material for the fixed scroll, the height of the wrap center part on the orbiting side is several tens of μ lower than the peripheral wrap part. The wrap height is tapered, and the familiar layer is uniform on the lap portion and the end plate portion of the orbiting scroll, or the familiar layer on the lap portion side with respect to the thickness of the familiar layer on the thrust sliding surface of the outer peripheral portion of the end plate. Attach so that the thickness is set to about twice as thick. Further, the present invention is characterized in that the familiar layer thickness attached to the wrap surface portion of the scroll is at least about the same as the amount of axial waviness of the end plate portion on the orbiting scroll side or the fixed scroll side. As described above, the outer peripheral portion of the scroll side scroll or fixed side is subjected to a surface hardening treatment on its thrust sliding surface and the scroll member of the scroll member having the familiar layer set on the surface of the other lap portion is provided with the surface hardening treatment. It is characterized by having a structure.

[0005]

In the present invention, the thrust sliding surface of the outer peripheral portion of the orbiting scroll is surface-hardened, or a wear resistant plate is incorporated into the thrust sliding surface of the outer peripheral portion of the orbiting scroll, and the wear resistant plate is used. Since the familiar layer is attached to the surface portion of, the wear of the thrust sliding surface on the outer peripheral portion of the end plate can be suppressed to a certain value. In addition, between the laps, the familiar layer thickness on the thrust sliding surface of the outer peripheral portion of the end plate, in other words, the familiar layer thickness on the lap side is larger (or thicker by about twice) with respect to the wear amount of that portion. Since it is set, abrasion does not progress to the base material of the base material at the lap portion. Therefore, a familiar layer is always present between both scrolls, and the gap adjusting function of relatively reducing the axial and radial gaps between the scrolls sufficiently works.

As described above, it is possible to solve the deterioration in the performance and reliability of the compressor due to the strong contact between the laps and the abnormal wear in the sliding parts due to the deformation during operation.

[0007]

EXAMPLE An example of the present invention is shown in FIGS. FIG. 1 is a perspective view showing an overall structure of an orbiting scroll 6 including a surface hardened layer 31 having a surface hardening treatment applied to a thrust sliding surface (a dimension of Lg) of an end plate outer peripheral portion 6a of the orbiting scroll 6. FIG. 2 is a partial cross-sectional view showing the structure of the outer peripheral portion of the orbiting scroll. For example, induction hardening treatment or nitriding treatment is performed on this portion, and lubricating alumite treatment (hard alumite treatment) is performed on the aluminum alloy. .. In FIG. 3, the familiar layers 32a and 32b are attached to the wrap portion 6b and the end plate portion 6a of the orbiting scroll 6, and the familiar layer thickness Lm on the thrust sliding surface of the outer peripheral portion of the end plate is set to the familiar layer in the axial direction on the side of the lap portion. In this example, the thickness is set smaller than Lk. In this case, the familiar layer thickness Lr in the radial direction is the familiar layer thickness Lm on the thrust sliding surface and the axial familiar layer thickness Lk on the lap portion side.
May be about the same. Practically, the thickness relationship will be Lk = Lr. In addition, in each of the examples, the number of spirals is omitted for clarity of explanation, and the familiar layer thickness is exaggerated in the drawing. The familiar layer 32 may be formed by surface coating (such as coating treatment of a molybdenum disulfide layer having excellent self-lubricating property). 4 and 5 show an embodiment in which a wear resistant plate 35 is incorporated in the thrust sliding surface of the outer peripheral portion 6a of the scroll plate, and the familiar layer 32a is attached to the surface part of the wear resistant plate 35. The wear resistant plate 35 is preferably made of a PK material having a hard surface and a very small surface roughness. In a scroll compressor composed of a scroll combination using a lightweight aluminum alloy for the orbiting scroll 6 and a cast iron material for the fixed scroll 5, as shown in FIG. 1 and FIG. Considering this, the height of the wrap center portion 6m on the turning side where the temperature rises is several tens of μs lower than that of the outer circumferential wrap portion 6n where the temperature becomes lower. There is. 6
f is a tapered surface. This structure has a wrap shape that matches the thermal deformation between both scrolls, mitigates the lap hit during driving, and combines the structure of the familiar layer described above to dramatically improve the conformability between laps. Can be improved. FIG. 6 is an explanatory diagram showing an example of distribution of the axial gap between the scroll laps before and after the operation when the orbiting scroll 6 of FIGS. 1 to 3 is operated in combination with the fixed scroll 5. The horizontal axis represents the scroll wrap winding angle (in the case of an involute curve, the expansion angle), and the vertical axis represents the fixed tooth bottom surface 5f, the orbiting scroll side tooth top surface (taper surface 6f) and the familiar layer 32.
The accuracy of the tip surface 32f of b is shown. Note that, on the fixed scroll 5 side, a familiar layer may be formed on the wrap surface and the end plate portion as in the orbiting side. FIG. 6 shows a case where the fixed scroll 5 is not subjected to surface treatment or a familiar layer. Further, the wrap height of the fixed scroll 5 is the same as the wrap height hs of the outer peripheral wrap portion 6n shown in FIG. 1 (strictly, it is the wrap height of the final end portion). That is, as shown in FIG. 6, the fixed scroll tooth bottom surface 5f has a uniform wrap depth (lap depth of hs) commensurate with the wrap height hs of the outer peripheral wrap portion 6n on the orbiting side. Between laps,
Since the familiar layer thickness on the thrust sliding surface of the outer peripheral part of the end plate, in other words, the familiar layer thickness on the lap side is set to be large (or about twice as thick) with respect to the wear amount of that part, Between the two scrolls, the familiar layer 32b (soft layer) is always present so that the abrasion does not proceed to the background of the base material 6b at the wrap portion on the turning side 6. Therefore, the gap adjusting function of relatively reducing the axial gap and the radial gap between the scrolls sufficiently works.
FIG. 7 shows that the thickness of the familiar layer 32b attached to the lap surface of the scroll is equal to or more than Lk = Rm, Lk> Rm with respect to the axial waviness amount Rm of the end plate portion 6a on the orbiting scroll 6 side. It is a longitudinal section showing an attached example. When a lightweight aluminum alloy is used for the orbiting scroll, due to its low rigidity, the end plate portion near the tooth bottom on the orbiting side undulates due to deformation during machining. This waviness amount is filled with the familiar layers 32b and 32c. Figure 8
FIG. 9 is a partial cross-sectional view showing a pattern in the case where both scrolls of orbit 6 and fixed 5 are combined. FIG. 9 is an embodiment in which the familiar layer thickness is set to a taper shape while the height hm of the wrap portion of the orbiting scroll is set to a constant value. The familiar layer 32 is a scroll compressor composed of a scroll combination using a lightweight aluminum alloy for the orbiting scroll 6 and a cast iron material for the fixed scroll 5, as described above. Considering the thickness Ld of the familiar layer 32d of the wrap center portion 6m on the turning side where the temperature becomes higher, the thickness Le of the familiar layer 32e of the outer peripheral lap portion 6n where the temperature becomes lower is set to be about twice as thick. It is attached. In this case, Ld = Lm
May be As shown in FIG. 9 and the like, the familiar layer 32 is formed only on the upper surface of the end plate portion or the side surface portion 6y.
No familiar layer is formed on the back side 6z of the end plate facing the back pressure chamber 41 (see FIG. 11). This is for dimensional control in the axial direction. Axial gap 11f in the outer peripheral portion of the end plate shown in FIG.
This is because it is convenient to manage the (small gap) to an appropriate gap of about several tens of μ during assembly. FIG. 10 is an explanatory diagram showing an example of distribution of axial gaps before and after operation when the orbiting scroll of FIG. 9 is used. By distributing the thickness on the familiar layer 32 side, the same operation and effect as shown in FIG. 6 can be obtained.

FIG. 11 is a vertical sectional view of a hermetic scroll compressor showing the entire structure of the present invention. Fixed scroll 5 with a gap adjustment function between the scroll wraps described above
Alternatively, the orbiting scroll 6 is arranged, and a cup-shaped oil level adjusting plate 51 capable of accumulating the fine solid substance 32y separated from the familiar layer 32 caused by the sliding contact of both scrolls is incorporated in the bottom chamber portion 2c. Here is an example. The upwardly convex conical oil level adjusting plate 51 includes an oil hole 51a and a cylindrical wall portion 51b capable of preventing the stirring action of the oil pipe 13a. By the filtering action of the oil level adjusting plate 51, it is possible to prevent the oil on the bottom of the chamber from being contaminated, so that it is possible to prevent foreign matter from entering the bearing. As a result, the life of the compressor can be further extended.

In FIG. 11, a compressor unit 100 is accommodated in the upper part of the closed container 1, and an electric motor unit 3 is accommodated in the lower part.
The closed container 1 is divided into an upper chamber 1a (discharge chamber) and electric motor chambers 1b and 1c.

In the compressor section 100, a fixed scroll member 5 and an orbiting scroll member 6 having a familiar layer 32 are meshed with each other to form a compression chamber (closed space) 7. The fixed scroll member 5 is composed of a disk-shaped end plate 5a and a wrap 5b which stands upright on the disk-shaped end plate 5a and is formed in an involute curve or a curve similar to this, and has a discharge port 10 at the center thereof and an intake port 16 at the outer peripheral portion thereof. Is equipped with. The orbiting scroll member 6 is composed of a disk-shaped end plate 6a, a wrap 6b standing upright on the end plate and having the same shape as the wrap of the fixed scroll, and a boss 6c formed on the non-lap surface of the end plate. The frame 11 has a bearing portion formed in the center thereof, and the rotary shaft 14 is supported by the bearing portion, and the eccentric shaft 14a at the tip of the rotary shaft is inserted into the boss 6c so as to be capable of turning motion. Also,
The fixed scroll member 5 is fixed to the frame 11 by a plurality of bolts, and the orbiting scroll member 6 is supported by the frame 11 by an Oldham mechanism 12 including an Oldham ring and an Oldham key.
Is formed so as to make a turning motion with respect to the fixed scroll member 5 without rotating. An electric motor shaft 14b fixed to the rotor 3b is integrally connected to the lower portion of the rotary shaft 14 to directly connect the electric motor unit 3. A vertical suction pipe 17 is connected to the suction port 16 of the fixed scroll member 5 through the closed container 1, and the upper chamber 1a in which the discharge port 10 is opened is connected to the upper electric motor chamber 1b through passages 18a and 18b. Is in communication with. The upper electric chamber 1b is a motor stator 3a.
And the side wall of the closed container 1 communicate with the lower electric motor chamber 1c. The upper electric motor chamber 1b communicates with a discharge pipe 20 that penetrates the closed container 1.

Reference numeral 22 denotes an oil sump at the bottom of the closed container. In the figure, the solid line arrow indicates the flow direction of the refrigerant gas, and the broken line arrow indicates the oil flow direction. It should be noted that reference numerals 8 and 21 are first and second balance weights for canceling the centrifugal force caused by the orbiting movement of the orbiting scroll 6.

Next, the flow of lubricating oil will be described with reference to FIG.

The lubricating oil 22a is stored in the lower part of the closed container 1 as an oil sump 22. The lower end of the rotary shaft 14 is provided with an eccentric shaft portion (crank pin) 14a, and the eccentric shaft portion 14a is a swivel bearing 39 in the boss portion 6c of the end plate 6a of the swivel scroll 6.
Through the orbiting scroll 6, which is a scroll compression element portion. A central vertical hole 13 for supplying oil to each bearing is formed in the rotary shaft 14 from the lower end to the upper end surface of the rotary shaft 14. Reference numeral 13a is a pumping oil pipe that connects the lower end of the rotary shaft 14 and the bottom oil sump 22. The main bearing 4
No. 0 is a highly reliable cylindrical roller bearing. A boss portion 6c of the orbiting scroll 6 is provided below the eccentric shaft portion 14a.
The balance weight 8 is formed integrally with the rotating shaft 14 at the upper part of the main bearing 40 facing the tip surface of the.
The oil pump pipe 13a immersed in the oil sump 22 of the lubricating oil 22a
Of the swirl bearing 39 (see FIG. 2) and the main bearing 40 on the downstream side, the pores 6e (see FIGS. 5 and 9) provided in the swivel end plate 6a are provided. ), An intermediate pressure Pm, which is a pressure in the middle of compression, is received, so that the lubricating oil 22a in the oil sump 22 at the bottom of the container rises in the central vertical hole 13 due to the pressure difference of (Pd-Pm). In this way, the oil is supplied to each bearing by the differential pressure oil supply method by the central vertical hole oil supply.

Lubricating oil 22a rising in the central vertical hole 13
Is supplied to the auxiliary bearing 9 and the slewing bearing 39. The oil supplied to the bearings 9, 39 flows into the back pressure chamber 41, and the oil flowing into the back pressure chamber 41 mixes with the refrigerant gas and flows out to the compression chamber 7 via the back pressure hole 6e. The oil that has reached the compression chamber 7 is pressurized together with the refrigerant gas and moves to the discharge chamber 1 a above the fixed scroll 5. In addition, the fine solid substance 32y separated from the acclimatization layer 32 caused by the sliding contact of both scrolls moves from the compression chamber 7 to the discharge chamber 1a together with the oil. Then, it moves to the electric motor room 1b. Further, the refrigerant gas and the oil are separated in the electric motor chamber 1b and the lower space 1c, and the oil drops into the oil sump 22 at the lower part of the closed container 1 and is again supplied to each sliding portion. On the other hand, fine solid substances 3
2y extends along the inner peripheral wall of the casing body 2b to the corner of a stackable cup-shaped oil level adjusting plate 51 incorporated in the bottom chamber 2c.

If an aluminum alloy, which is a lightweight material, is used for the orbiting scroll 6, it is advantageous for increasing the speed of the compressor. That is, this is because the centrifugal force acting on the slewing bearing portion is reduced, and the bearing loss is further reduced and the performance and reliability are further improved. FIG. 12 shows an example in which only the surface hardening treatment is applied to the thrust sliding surface of the outer peripheral portion of the orbiting scroll, while the familiar layer is attached to the wrap portion of the orbiting scroll.

[0016]

The present invention has the following effects.

(1) The wear of the thrust sliding surface on the outer peripheral portion of the end plate can be suppressed to a certain value, and the wear does not progress to the ground of the base material at the lap portion. Therefore, the gap adjusting function that the familiar layer is always present between the scrolls to relatively reduce the axial and radial gaps between the scrolls sufficiently works.

(2) The strong contact between the laps due to the deformation during operation and the abnormal wear in the sliding parts are suppressed, and the sliding performance and the conformability between the scroll laps are greatly improved. And the reliability can be greatly improved.

(3) Since the oil at the bottom of the chamber can be prevented from being contaminated, foreign matter can be prevented from being mixed into the bearing portion, and the life of the compressor can be further extended.

(4) When a lightweight aluminum alloy is used for the orbiting scroll, the operating range in the high speed range is wider, and by avoiding a strong hit between the laps, the entire compressor during high speed operation can be avoided. Has the ripple effect of reducing vibration and noise.

[Brief description of drawings]

FIG. 1 is a perspective view showing the overall structure of an orbiting scroll.

FIG. 2 is a partial cross-sectional view showing the structure of the outer peripheral portion of the orbiting scroll.

FIG. 3 is a partial cross-sectional view showing the structure of the outer peripheral portion of the orbiting scroll end plate.

FIG. 4 is a perspective view showing the overall structure of an orbiting scroll.

FIG. 5 is a vertical sectional view of an orbiting scroll.

FIG. 6 is an explanatory diagram showing an example of distribution of axial gaps before and after operation.

FIG. 7 is a vertical cross-sectional view showing an example in which the familiar layer thickness attached to the wrap surface portion of the scroll is equal to or more than the same.

FIG. 8 is a partial cross-sectional view showing a pattern in the case of combining both a turning scroll and a fixed scroll.

FIG. 9 is a vertical sectional view of an orbiting scroll.

10 is an explanatory diagram showing an example of distribution of axial gaps before and after operation when the orbiting scroll of FIG. 9 is used.

FIG. 11 is a vertical cross-sectional view of a hermetic scroll compressor showing the overall configuration of the present invention.

FIG. 12 is a longitudinal sectional view of an orbiting scroll in an example in which only the surface hardening treatment is applied to the thrust sliding surface of the end plate of the orbiting scroll and the wrap portion of the orbiting scroll is provided with a familiar layer.

FIG. 13 is an explanatory view showing meshing patterns between scroll members in a state in which the entire surface of the scroll wrap portion and the end plate portion is made of a material that easily wears, in an example of a conventional technique.

[Explanation of symbols]

1b ... Electric motor room, 5 ... Fixed scroll, 6 ... Orbiting scroll, 6a ... End plate part, 22a ... Oil, 31 ... Surface hardening layer,
32 ... Familiar layer, 35 ... Abrasion resistant plate, 51 ... Oil level adjusting plate.

Claims (1)

Claim: What is claimed is: 1. A fixed scroll member and an orbiting scroll member for upstanding a spiral wrap on a disk-shaped end plate are engaged with each other with the wrap inside, and the orbiting scroll member is connected to a rotary shaft. Engaging with an eccentric shaft portion to cause the orbiting scroll member to orbit with respect to the fixed scroll member without rotating, and the fixed scroll member has a discharge port opening to the central portion and an intake port opening to the outer peripheral portion. A gas is sucked from the suction port, moved around a compression space formed by both scroll members to reduce the volume and compresses the gas, and a compressed gas is discharged from the discharge port at the center of the end plate portion of the fixed scroll member. In a scroll compressor that discharges the orbiting scroll, a surface hardening treatment is applied to the thrust sliding surface of the outer peripheral portion of the end plate of the orbiting scroll, and A scroll is characterized in that a familiar layer is attached to the end portion and the end plate portion, and the thickness of the familiar layer on the thrust sliding surface of the outer peripheral portion of the end plate is set smaller than the thickness of the familiar layer on the side of the lap portion. Compressor.