CN116348677A

CN116348677A - Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Info

Publication number: CN116348677A
Application number: CN202180065735.0A
Authority: CN
Inventors: 梅钵佑介; 安田文昭; 达胁浩平
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2020-10-01
Filing date: 2021-09-22
Publication date: 2023-06-27
Also published as: JPWO2022071039A1; DE112021005143T5; GB2611698A; JP7442668B2; WO2022071039A1; GB2611698B; GB202300713D0; GB202407600D0; GB2627160A

Abstract

The device is provided with: a crankshaft (6) supported by a bearing fixed to the housing (1); a drive mechanism unit (4) for a crankshaft (6); a swing scroll (32) provided on an eccentric shaft portion (62) of a crankshaft (6); and a fixed scroll (31) provided in the housing (1), wherein a balancer portion (61B) is provided in a main shaft portion (61) of the crankshaft (6), and the balancer portion (61B) reduces unbalanced force accompanying rotation of the crankshaft (6) and is formed as a single body.

Description

Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Technical Field

The present application relates to scroll compressors.

Background

The crankshaft of a scroll compressor is sometimes provided with a counterweight to balance the centrifugal force and moment generated about the shaft. As an example of this, the following technique is disclosed: the present invention provides a rotary shaft and a balance weight having an annular outer peripheral surface fixed to the rotary shaft and rotating together with the rotary shaft, wherein a recess for adjusting an angular position of the balance weight with respect to the rotary shaft is formed in a part of the outer peripheral surface, and deflection of the rotary shaft is suppressed by the balance weight in such a configuration (for example, refer to patent document 1).

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open publication 2016-50551

Disclosure of Invention

Problems to be solved by the invention

However, the technique disclosed in patent document 1 has a problem in that a balance weight corresponding to a rotation shaft is selected, the angle of the balance weight is adjusted, and then the balance weight is attached to the rotation shaft, as follows: there is a risk of installing a wrong balancing weight; there is a concern that an angular offset occurs when installing the balance weight, and in order to prevent this, a high level of assembly devices and tools are required, requiring a complicated assembly work; further, since the balance weight is press-fitted into the rotary shaft, it is necessary to perform high-level processing and to provide a ring for press-fitting, which leads to an increase in the weight of the balance weight.

The present application discloses a technique for solving the above-described problems, and an object thereof is to provide a scroll compressor which is easy to assemble and small in size.

Means for solving the problems

The scroll compressor disclosed in the present application comprises: a crankshaft supported by a bearing fixed to the housing; a drive unit for the crankshaft; a swing scroll provided on an eccentric shaft portion of the crankshaft; and a fixed scroll provided in the housing, wherein a balancer portion is provided in a main shaft portion of the crankshaft, and the balancer portion reduces unbalanced force accompanying rotation of the crankshaft, and is formed as a single body.

Effects of the invention

The scroll compressor disclosed in the present application has the above-described configuration, and therefore has an effect of providing a scroll compressor that is easy to assemble and small.

Drawings

Fig. 1 is a perspective view of a scroll compressor according to embodiment 1.

Fig. 2 is a cross-sectional view of the scroll compressor according to embodiment 1.

Fig. 3A in fig. 3 is a side view of the crankshaft of embodiment 1, and fig. 3B is a top view of the crankshaft of embodiment 1.

Fig. 4A in fig. 4 is a side view of the crankshaft of embodiment 1, and fig. 4B is a sectional view of the crankshaft shown in fig. 4A taken along line A-A.

Fig. 5A in fig. 5 is a side view of another crankshaft according to embodiment 1, and fig. 5B is a sectional view of another crankshaft shown in fig. 5A taken along line A-A.

Fig. 6A in fig. 6 is a side view of the crankshaft of embodiment 2, and fig. 6B is a top view of the crankshaft of embodiment 2.

Fig. 7A in fig. 7 is a side view of the crankshaft of embodiment 2, and fig. 7B is a sectional view of the crankshaft shown in fig. 7A taken along line A-A.

Fig. 8A in fig. 8 is a side view of the crankshaft of embodiment 3, and fig. 8B is a top view of the crankshaft of embodiment 3.

Fig. 9A in fig. 9 is a side view of the crankshaft of embodiment 3, and fig. 9B is a sectional view of the crankshaft shown in fig. 9A taken along line A-A.

Fig. 10A in fig. 10 is a side view of the crankshaft of embodiment 4, and fig. 10B is a top view of the crankshaft of embodiment 4.

Fig. 11A in fig. 11 is a side view of the crankshaft of embodiment 4, and fig. 11B is a sectional view of the crankshaft shown in fig. 11A taken along line A-A.

Fig. 12A in fig. 12 is a side view of the crankshaft of embodiment 5, and fig. 12B is a top view of the crankshaft of embodiment 3.

Fig. 13A in fig. 13 is a side view of the crankshaft of embodiment 5, and fig. 13B is a sectional view of the crankshaft shown in fig. 13A taken along line A-A.

Fig. 14A in fig. 14 is a side view of another crankshaft according to embodiment 5, and fig. 14B is a sectional view of the crankshaft shown in fig. 14A taken along line A-A.

Fig. 15 is a partial enlarged view of a compression driving unit of the scroll compressor according to embodiment 6.

Fig. 16 is a diagram showing the structure of the balancer parts in the X-Y coordinate system of fig. 9A.

Fig. 17 is a diagram showing the structure of the balancer parts in the X-Y coordinate system of fig. 11A.

Fig. 18A in fig. 18 is a diagram showing another structure of the balancer parts in the X-Y coordinate system of embodiment 4, fig. 18B is a diagram showing another structure of the balancer parts in the X-Y coordinate system of embodiment 4, fig. 18C is a diagram showing another structure of the balancer parts in the X-Y coordinate system of embodiment 4, and fig. 18D is a diagram showing another structure of the balancer parts in the X-Y coordinate system of embodiment 4.

Fig. 19A in fig. 19 is a side view of the crankshaft of embodiment 7, and fig. 19B is a sectional view of the crankshaft shown in fig. 19A taken along line A-A.

Fig. 20A in fig. 20 is a side view of the crankshaft of embodiment 8, and fig. 20B is a top view of the crankshaft of embodiment 8.

Fig. 21 is a cross-sectional view of the scroll compressor according to embodiment 8.

Fig. 22 is a partial cross-sectional view of the scroll compressor according to embodiment 8.

Fig. 23 is a partial cross-sectional view of another scroll compressor of embodiment 8.

Fig. 24 is a diagram showing another configuration of the balancer parts in the X-Y coordinate system of the scroll compressor of embodiment 1.

Fig. 25 is a cross-sectional view showing the shape of a member before forming a balancer portion of the scroll compressor of embodiment 4.

Fig. 26A in fig. 26 is a diagram showing another structure of a balancer part in the X-Y coordinate system of embodiment 4, fig. 26B is a diagram showing another structure of a balancer part in the X-Y coordinate system of embodiment 4, fig. 26C is a diagram showing another structure of a balancer part in the X-Y coordinate system of embodiment 4, and fig. 26D is a diagram showing another structure of a balancer part in the X-Y coordinate system of embodiment 4.

Detailed Description

Embodiment 1.

Embodiment 1 will be described below with reference to the drawings. Fig. 1 is a perspective view of a vertical scroll compressor 100. Fig. 2 is a cross-sectional view of the scroll compressor 100 in a vertical direction, wherein the U side represents the upper side and the L side represents the lower side. In addition, the U side and the L side shown in the other figures refer to the U side and the L side in fig. 2. Note that this relationship is the same in the following embodiments, and therefore, the description thereof is appropriately omitted.

As shown in fig. 1 and 2, the scroll compressor 100 includes the following components as main components: a housing 1 composed of a middle housing 11, an upper housing 12, and a lower housing 13; a crankshaft 6 supported by a bearing of the middle housing 11; a driving unit 4 that rotationally drives a crankshaft 6; and a compression driving unit 3 provided with a fixed scroll 31 and a swing scroll 32.

An outline of the operation of the scroll compressor 100 having such a configuration will be described. By the operation of the driving portion 4, the crankshaft 6 rotates, and the refrigerant flows into the compression driving portion 3 through the 1 st frame 2. Here, the orbiting scroll 32 provided on the eccentric shaft portion 62 of the crankshaft 6 performs an orbiting motion, and the refrigerant is compressed in the compression chamber 34. The compressed refrigerant flows to the discharge pipe 15 through the fixed scroll 31.

A balancer housing 301 is provided in a balancer portion 61B described later, and the balancer portion 61B is provided between the 1 st frame 2 and the main shaft portion 61, which are disposed on the L side of the orbiting scroll 32. The balancer housing 301 has the following functions: the refrigerating machine oil that has risen in the scroll compressor 100 together with the refrigerant through the oil passage 60 described later is retained, and outflow of the refrigerating machine oil to the outside of the scroll compressor 100 is suppressed, whereby a decrease in heat exchange capacity of a heat exchanger connected to the scroll compressor 100 is suppressed. The balancer housing 301 is fixed to the 1 st frame 2 by bolts or the like.

Hereinafter, fig. 3A and 3B show a crankshaft 6 provided with a balancer portion 61B as the gist of the present application, and the balancer portion 61B is formed of a single body for reducing unbalanced force accompanying rotation of the crankshaft 6. Fig. 3A is a side view of the crankshaft of embodiment 1, and fig. 3B is a plan view of the crankshaft of embodiment 1 as viewed from the U side (arrow Z) of fig. 3A. In addition, fig. 4A shows an enlarged view of the balancer portion 61B of fig. 3A, and fig. 4B shows a sectional projection view of the line A-A of fig. 4A.

As shown in fig. 4, in the coordinate system on the plane perpendicular to the rotation axis 6CL of the crankshaft 6, a line on the horizontal plane including the rotation axis 6CL is set as the X axis, the vertical center line of the crankshaft 6 perpendicular to the X axis is set as the Y axis, and a point on the rotation axis 6CL where the X axis intersects with the Y axis is defined as the origin C. Further, the balancer portion 61B has a balancer-side weight portion 612A and a balancer-opposite-side weight portion 612B as the weight portion 612, and the balancer-side weight portion 612A and the balancer-opposite-side weight portion 612B are provided so as to be continuous on a plane including the rotation shaft 6CL of the crankshaft 6.

The balancer-side weight 612A is formed in the 1 st quadrant and the 2 nd quadrant in the X-Y coordinate system defined in the above, and the balancer-opposite-side weight 612B is formed in the 3 rd quadrant and the 4 th quadrant. In embodiment 1 and other embodiments, the relationship between the X-axis, the Y-axis, the origin C, the crankshaft 6, and the rotation shaft 6CL, and the relationship between the balancer-side weight 612A and the balancer-opposite-side weight 612B are the same, and therefore, the description of the relationship is appropriately omitted. The 1 st quadrant, the 2 nd quadrant, the 3 rd quadrant, and the 4 th quadrant are only shown in fig. 4B, and the description thereof is omitted in other similar drawings.

In fig. 3A, the crankshaft 6 includes an oil passage 60, a main shaft portion 61, and an eccentric shaft portion 62. The main shaft portion 61 is a main portion of the crankshaft 6, and the rotary shaft 6CL is arranged to coincide with the shaft center line of the middle housing 11 shown in fig. 2. The eccentric shaft portion 62 is provided on the U side of the crankshaft 6 such that the eccentric shaft 62CL is eccentric with respect to the rotation shaft 6CL of the main shaft portion 61.

The oil passage 60 is provided in the crankshaft 6 so as to extend from the L-side end to the U-side end. Although the oil passage 60 is provided along the rotation axis 6CL of the crankshaft 6 in fig. 3A, the present invention is not limited thereto, and the oil passage 60 may be provided below the X axis in fig. 4B.

The main shaft portion 61 includes a main bearing portion 61A, a balancer portion 61B, a rotor press-fit portion 61C, and a sub-bearing portion 61D in this order from the U side. The rotor press-fit portion 61C is provided with a rotor 4A of the driving portion 4 shown in fig. 2. The main bearing portion 61A is inserted into the bearing portion 2A of the 1 st frame 2. The sub bearing portion 61D is inserted into the sub bearing portion 5A of the 2 nd frame 5. As shown in fig. 2, a sleeve bearing 65 that is driven by the rotation of the crankshaft 6 is provided between the bearing portion 2A of the 1 st frame 2 and the main bearing portion 61A of the crankshaft 6.

As shown in fig. 4B, in the weight portion 612 forming the balancer portion 61B, a smoothly semicircular balancer-side weight portion 612A having a radius R1max is provided in the 1 st and 2 nd quadrants of the X-Y coordinate system, and a smoothly semicircular balancer-opposite-side weight portion 612B having a radius R2max is provided in the 3 rd and 4 th quadrants. That is, a balancer-side weight 612A and a balancer-opposite-side weight 612B are provided in series on the Y axis. The balancer-side weight 612A and the balancer-opposite-side weight 612B are identified by making the radius R1max > the radius R2 max. That is, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are formed according to the magnitude relation between the weight and the center of gravity position. In the case of the configuration shown in fig. 4, the radius R1max is the maximum distance from the origin C of the balancer-side weight 612A, and the radius R2max is the maximum distance from the origin C of the balancer-opposite-side weight 612B.

Here, the 1 st center of gravity 61G of the balancer-side weight portion 612A and the 2 nd center of gravity 62C of the balancer-opposite-side weight portion 612B are shown. The 1 st center of gravity 61G of the balancer-side weight 612A and the 2 nd center of gravity 62C of the balancer-opposite-side weight 612B exist on the Y axis because the weight 612 has a semicircular shape that is symmetrical and rounded about the Y axis. The flange 611 provided in the balancer 61B will be described later.

The planar shape and dimensions of the balancer-side weight 612A and the balancer-opposite-side weight 612B are set according to the specifications (capacity, size, rotation speed, etc.) of the scroll compressor 100, and a rounded semicircle is not necessarily adopted. Further, it is important as the balancer that the product of "the distance of the center of gravity of the balancer from the rotation axis 6CL (the distance from the origin C in the coordinate system on the X-Y axis corresponds thereto)" and "the weight of the balancer" is large. If this distance is increased, the weight can be reduced, but the space size becomes large.

In embodiment 1, in order to form a relationship of "weight of balancer-side weight > weight of balancer-opposite-side weight", for example, a weight ratio of balancer-side weight 612A to balancer-opposite-side weight 612B is set to, for example, 4:1. that is, the area ratio in at least 1 or more cross sections perpendicular to the rotation axis 6CL is set to, for example, 4:1. that is, the area in the cross section perpendicular to the rotation shaft 6CL has a relationship of "the area of the balancer-side weight portion 612A > the area of the balancer-opposite-side weight portion 612B". Thus, a relationship of "the weight of the balancer-side weight portion 612A > the weight of the balancer-opposite-side weight portion 612B" can be easily obtained.

Next, in fig. 4B, the reason why "max" described as, for example, radius R1max and radius R2max is used will be described. The radius R1max of the balancer-side weight 612A and the radius R2max of the balancer-opposite-side weight 612B are rounded. However, the present invention is not limited thereto, and for example, the balancer-side weight portion 612A and the balancer-opposite-side weight portion 612B may have a circular arc shape having an elliptical shape or a concave-convex shape in part (this example is shown using fig. 24 in the following description). In this case, the radius R1max is a portion corresponding to the maximum distance of the balancer-side weight 612A, and the radius R2max is a portion corresponding to the maximum distance of the balancer-opposite-side weight 612B.

Thus, "max" is used in consideration of such a circular arc shape having an elliptical shape or a concave-convex shape. Note that the arc shape of the balancer portion 61B is the same as the arc shape having an elliptical shape or a concave-convex shape locally, and therefore, the description thereof will be omitted appropriately in the following embodiments. Here, the relationship with the diameter d 1/2 of the main bearing portion 61A, that is, the relationship with d/2 has a relationship with the radius R2max not less than d/2, but in embodiment 1, the radius R2max of the balancer portion 61B is set to be large.

As shown in fig. 3 and 4, the balancer portion 61B is constituted by a weight portion 612, and the weight portion 612 has a shape in which a flange portion 611 having a semicircular planar shape, a semicircular balancer-side weight portion 612A having a radius R1max, and a semicircular balancer-opposite-side weight portion 612B having a radius R2max are connected. In the flange portion 611 shown in fig. 4, the distance 611Rmin from the rotation shaft 6CL to the outermost diameter is set to be larger than d/2 of the main bearing portion 61A. I.e. has a relationship of distance 611Rmin > d/2. In addition, the relationship between the distance 611Rmin and the radius R1max of the balancer-side weight 612A is set to be that the distance 611Rmin < the radius R1max, but is not limited thereto.

The flange 611 has a function of supporting a bearing provided between the crankshaft 6 and the 2 nd frame 5 in the axial direction.

Another example will be described with reference to the drawings. Fig. 5A is a side view of another crankshaft according to embodiment 1, and fig. 5B is a sectional view of another crankshaft shown in fig. 5A, taken along line A-A. In fig. 5B, the balancer-side weight portion 612A is a semicircle having a straight line portion LC1 in the vertical direction at a distance L1 from the Y axis in the 1 st quadrant, and the balancer-opposite-side weight portion 612B is a semicircle having a straight line portion LC2 in the Y axis direction at a distance L2 from the Y axis in the 4 th quadrant. The term "predetermined value or object" is also the same as the term "predetermined value or object" in the following description, and therefore, the description thereof is appropriately omitted. Further, the 2 nd center of gravity 62C of the counter balance weight 612B and the 1 st center of gravity 61G of the counter balance weight 612A have an angle θ with the origin C as the center.

The straight line LC1 is a side formed parallel to the Y axis. In the present application, "side" means "a portion formed in a straight line". This content is the same as in the following embodiments, and therefore, the description thereof is appropriately omitted. The straight line LC2 formed in the balancer opposing weight 612B corresponds to 1 in the 1 st side of either or both of the 3 rd and 4 th quadrants of the X-Y coordinate system, and here corresponds to the 1 st side formed in the 4 th quadrant. Further, the linear portion LC2 is formed parallel to the Y axis.

In addition, the above-described parallelism includes strict parallelism, and of course also includes parallelism including an error range in processing. Note that this parallelism is the same in the following embodiments, and therefore, the description thereof is appropriately omitted.

In fig. 5B, the straight line portion LC1 is provided in the 1 st quadrant and the straight line portion LC2 is provided in the 4 th quadrant, but these may be formed in the balancer portion 61B provided in the 2 nd and 3 rd quadrants, respectively, or these may be combined. In addition, regarding the planar shape of the flange portion 611, although it is formed in a semicircular shape in consideration of workability, since the flange portion 611 functions to support the sleeve bearing 65, it is not limited to a semicircular shape.

Next, the positional relationship between the 1 st center of gravity 61G of the balancer-side weight portion 612A and the 2 nd center of gravity 62C of the counter-balancer-side weight portion 612B will be described with reference to fig. 5B. The planar shape of the balancer portion 61B is not a rounded semicircular shape as described above, and is applicable to the following description. In the X-Y coordinate system passing through the 1 st center of gravity 61G of the balancer-side weight portion 612A and perpendicular to the rotation axis 6CL of the crankshaft 6, the angle θ formed by the line passing through the 1 st center of gravity 61G of the balancer-side weight portion 612A and the origin C and the line passing through the 2 nd center of gravity 62C of the balancer-opposite-side weight portion 612B and the origin C is preferably set to 180 degrees, at least to 90 degrees to 270 degrees. For the above angle θ, fig. 5B shows an example thereof.

In fig. 4B, in an X-Y coordinate system passing through the 1 st gravity center 61G of the balancer-side weight portion 612A of the balancer portion 61B and perpendicular to the rotation axis 6CL of the crankshaft 6, the X-Y coordinate system is divided into two by a line perpendicular to a line connecting the 1 st gravity center 61G of the balancer-side weight portion 612A and a point passing through the rotation axis 6CL, in this case, an X-axis, and the side where the 1 st gravity center 61G is located is the balancer-side weight portion 612A and the side where the other 2 nd gravity center 62C is located is the balancer-opposite-side weight portion 612B. In the cross-sectional shape of the balancer portion 61B of the crankshaft 6 in the X-Y coordinate system, when the maximum distance from the origin C is set to be the radius R1max of the arc of the balancer-side weight portion 612A and the radius R2max of the arc of the balancer-opposite-side weight portion 612B, the former is set to be large.

Radius R1max > radius R2max

On the L side of the crankshaft 6 shown in fig. 2, a balancer 66 is provided to cancel out unbalance caused by the swing of the swing scroll 32. The crankshaft 6 is formed integrally with a forged steel material, a cast steel material, or an alloy obtained by sintering a metal powder, and is finished into a predetermined shape and size by machining, for example, N/C (Numerical Control: numerical control) machining, at all portions including the balancer portion 61B provided as a single body. Further, the balancer portion 61B may be subjected to additional processing to improve the balance of the scroll compressor 100.

The scroll compressor 100 having the crankshaft 6 with the above-described configuration is configured to prevent seizure and wear of the bearings by canceling the centrifugal force of the orbiting scroll 32 that performs the eccentric orbiting motion by the rotation of the balancer portion 61B provided in the crankshaft 6. Further, since the balancer portion 61B is provided as an integral body to the crankshaft 6, the ring portion for thermocompression bonding can be eliminated, and therefore the weight portion 612 can be miniaturized and the rigidity of the crankshaft 6 can be improved.

Further, since the scroll compressor 100 is structured as described above, it is not necessary to install a counterweight, and therefore, the scroll compressor 100 can be assembled easily and in a short time, and thus, an inexpensive scroll compressor 100 can be provided. Further, since the rigidity of the crankshaft 6 is improved, the reliability of the scroll compressor 100 is improved, and the compression amount of the refrigerant can be increased and the use rotational speed can be increased. As shown in fig. 2, a sleeve bearing 65 can be provided between the bearing portion 22 of the 1 st frame 2 and the main bearing portion 61A of the crankshaft 6, thereby further improving reliability.

Further, by machining all parts of the crankshaft 6 including the balancer portion 61B, the weight and the center of gravity can be controlled with high accuracy, and the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, so that the vibration is small, and the reliability can be improved.

Further, by providing the balancer-side weight 612A and the counter balancer-side weight 612B on the X-Y coordinate system including the rotation shaft 6CL of the crankshaft 6, which is the Y-axis in this case, for example, in the case shown in fig. 4, the balancer-side weight 612A and the counter balancer-side weight 612B can be formed in symmetrical shapes with respect to the X-Y coordinate system, and control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved.

Further, the balancer portion 61B is formed in a semicircular shape with the origin C as a center, so that the flange portion 611, the balancer-side weight portion 612A, and the balancer-opposite-side weight portion 612B can be machined simultaneously with other portions of the crankshaft 6. Since machining can be performed simultaneously, control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved.

Further, since the distance 611Rmin from the rotation shaft 6CL to the outermost diameter is formed larger than d/2 of the main bearing portion 61A, the diameter of the balancer portion 61B becomes larger, rigidity can be improved, and reliability can be improved.

As shown in fig. 24, a part of the outer shape of the counter balance weight 612B may be formed in an elliptical shape 612BB. Then, sides S22 and S23 are formed. The sides S22 and S23 formed in the balancer opposing side weight 612B correspond to 1 of the 1 st sides formed in either or both of the 3 rd and 4 th quadrants of the X-Y coordinate system, the side S22 corresponds to the 1 st side formed in the 4 th quadrant, and the side S23 corresponds to the 1 st side formed in the 3 rd quadrant. In addition, sides S22 and S23 are formed parallel to the Y axis. In this way, if the elliptical shape 612BB is formed or alternatively formed in a concave-convex shape (having a concave-convex shape on the surface), the total weight of the balancer portion 61B can be reduced, and the weight portion 612 can be miniaturized.

The angle θ formed by the line passing through the 1 st center of gravity 61G and the origin C of the balancer-side weight portion 612A and the line passing through the 2 nd center of gravity 62C and the origin C of the balancer-side weight portion 612B is preferably 180 degrees, at least 90 degrees or more and 270 degrees or less, whereby the weight of the balancer-side weight portion 612B can be reduced, and the weight portion 612 can be miniaturized. Further, since the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, the vibration is small, and the reliability can be improved.

In the above description, for simplicity, the 2 nd center of gravity 62C of the counter balance weight 612B is necessarily present in the X-Y coordinate system passing through the 1 st center of gravity 61G of the counter balance weight 612A and perpendicular to the rotation axis 6CL of the crankshaft 6, but the present invention is not limited thereto, and in the case where the 2 nd center of gravity 62C of the counter balance weight 612B is not present in the X-Y coordinate system, it is conceivable to replace the 2 nd center of gravity 62C with a point obtained by transferring the point to the X-Y coordinate system along the rotation axis 6 CL. This is the same as in the following embodiments, and therefore, the description thereof is appropriately omitted.

According to the scroll compressor of embodiment 1 constructed as described above,

the device is provided with: a crankshaft supported by a bearing fixed to the housing; a drive unit for the crankshaft; a swing scroll provided on an eccentric shaft portion of the crankshaft; and a fixed scroll provided in the housing, wherein a balancer portion is provided in a main shaft portion of the crankshaft, the balancer portion reducing unbalanced force accompanying rotation of the crankshaft and being formed as a single body,

therefore, the unbalanced force accompanying the rotation of the crankshaft can be reduced by the balancer portion, so that the assembly work is easy and the downsizing can be achieved.

Furthermore, according to the scroll compressor of embodiment 1,

the balancer section includes a balancer-side weight section and a balancer-opposite-side weight section that are disposed in series on a plane including a rotation axis of the crankshaft, and,

in order to form a relationship that the weight of the balancer-side weight portion > the weight of the balancer-opposite-side weight portion, an area in at least 1 or more cross sections perpendicular to the rotation axis has

The relationship that the area of the balancer-side weight is greater than the area of the balancer-opposite-side weight,

therefore, by merely providing the relationship in which the area of the balancer-side weight portion is larger than the area of the balancer-opposite-side weight portion, a balancer portion capable of reducing unbalanced force accompanying rotation of the crankshaft can be obtained easily.

Furthermore, according to the scroll compressor of embodiment 1,

in a coordinate system on a plane perpendicular to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is set as an X axis, a longitudinal center line of the crankshaft perpendicular to the X axis is set as a Y axis, and a point on the rotation axis at which the X axis intersects the Y axis is defined as an origin,

The balancer opposite side weight has a 1 st side in either or both of the 3 rd and 4 th quadrants of the coordinate system,

thus, by forming the 1 st side,

the relationship of the area of the balancer weight > the area of the balancer weight opposite to the balancer can be obtained easily.

Furthermore, according to the scroll compressor of embodiment 1,

the 1 st side is formed by a side parallel to the Y axis,

therefore, machining can be performed by a general-purpose machine such as a 2-axis lathe. Further, since machining can be performed simultaneously with other portions, control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved. In addition, since the processing can be performed by general-purpose machines, the equipment investment is small, and low cost can be realized.

Furthermore, according to the scroll compressor of embodiment 1,

the balancer-side weight has a side parallel to the Y axis with a distance L1 from the Y axis in any one of the 1 st and 2 nd quadrants of the coordinate system,

the 1 st side of the balancer opposite side weight has a 1 st side parallel to the Y axis with a distance L2 from the Y axis,

Formed in a relationship of distance L1 > distance L2, and the parallel side and the parallel 1 st side are formed on the same side with respect to the Y axis,

therefore, the relationship of the area of the balancer-side weight portion > the area of the balancer-opposite-side weight portion can be obtained simply and reliably.

Further, the machining can be performed by a general-purpose machine such as a 2-axis lathe. Further, since machining can be performed simultaneously with other portions, control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved. In addition, since the processing can be performed by general-purpose machines, the equipment investment is small, and low cost can be realized.

Furthermore, according to the scroll compressor of embodiment 1,

the balancer-side weight and the balancer-opposite-side weight have a semicircle centered on the origin, a maximum distance of the semicircle from the origin being such that

A relationship that a maximum distance of the balancer side weight is greater than a maximum distance of the balancer opposite side weight is formed,

Furthermore, according to the scroll compressor of embodiment 1,

a part of the external shape of the counterweight part at the opposite side of the balancer is formed in an elliptic shape or a concave-convex shape,

therefore, the total weight of the balancer section can be reduced, and miniaturization can be achieved.

Furthermore, according to the scroll compressor of embodiment 1,

with the origin point as the center of the device,

an angle formed by a line passing through the 1 st gravity center of the balancer-side weight and the origin and a line passing through the 2 nd gravity center of the balancer-opposite-side weight and the origin is 90 degrees or more and 270 degrees or less,

therefore, the weight of the counterweight portion on the opposite side to the balancer can be reduced, and miniaturization can be achieved. Further, since the centrifugal force of the orbiting scroll can be offset with high accuracy, the vibration is small, and the reliability can be improved.

Furthermore, according to the scroll compressor of embodiment 1,

the balancer portion is provided with a flange portion which is connected to the balancer-side weight portion in the axial direction,

Therefore, the balancer section can be easily supported by the flange section at other locations.

Furthermore, according to the scroll compressor of embodiment 1,

the entire shape of the crankshaft is formed by machining,

therefore, the center of gravity can be easily controlled, and the centrifugal force of the orbiting scroll can be offset with high accuracy, so that the vibration is small, and the reliability can be improved.

In the following embodiment, the same applies to the following aspect as in embodiment 1:

a balancer part is provided on a main shaft part of a crankshaft, the balancer part reduces unbalanced force accompanying rotation of the crankshaft, and is formed as a single body,

in the X-Y coordinate system of the system,

has a relationship that the area of the balancer-side weight is > the area of the balancer-opposite-side weight,

therefore, the description thereof is appropriately omitted.

Embodiment 2.

Next, a crankshaft 6 according to embodiment 2 will be described with reference to the drawings. Fig. 6A is a side view of the crankshaft of embodiment 2, and fig. 6B is a plan view of the crankshaft of embodiment 2 as viewed from the U side (arrow Z) of fig. 6A. In addition, fig. 7A shows an enlarged view of the balancer portion 61B of fig. 6A, and fig. 7B shows a sectional projection view of the line A-A of fig. 6A. In the drawings, the same portions as those in embodiment 1 are denoted by the same reference numerals, and description thereof is omitted.

As shown in the drawings, the balancer portion 61B is not provided with the flange portion 611 shown in fig. 3A and 3B in embodiment 1. That is, the balancer portion 61B is provided with a balancer-side weight portion 612A and a balancer-opposite-side weight portion 612B. Otherwise, the same as in embodiment 1 is applied. With this configuration, the effect of miniaturization and weight reduction is further achieved in accordance with embodiment 1. In addition, in the case of embodiment 2, since the sleeve bearing 65 is not supported, instead, the bearing portion 2A of the 1 st frame 2 is processed or the bearing is provided by press fitting or the like, thereby forming a bearing corresponding to the main bearing portion 61A.

In the case of the shape shown in fig. 7B, the shape can be formed by forging or casting, and thus, the shape can be formed without cutting. This is the same as in the case shown in fig. 4B of embodiment 1. In the case of fig. 5B of embodiment 1, the linear portions LC1 and LC2 can be formed by cutting from the state shown in fig. 4B.

According to the scroll compressor of embodiment 2 configured as described above, the same effects as those of the above-described embodiment are achieved, and,

Since the flange portion is not provided, miniaturization and weight reduction can be achieved.

Embodiment 3.

Next, a crankshaft 6 according to embodiment 3 will be described with reference to the drawings. Fig. 8A is a side view of the crankshaft of embodiment 3, and fig. 8B is a plan view of the crankshaft of embodiment 3 as viewed from the U side (arrow Z) of fig. 8A. In addition, fig. 9A shows an enlarged view of the balancer portion 61B of fig. 8A, and fig. 9B shows a sectional projection view of the line A-A of fig. 9A. In fig. 16, the 1 st side formed in either or both of the 3 rd and 4 th quadrants of the X-Y coordinate system will be described. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 9, the planar shape of the counter balance weight 612B is set to be square formed by the straight portion 612S. The square shape of the balancer opposing weight portion 612B is a shape in which the linear portion 612S having the width W1 is connected at a position of the linear portion 612S at a distance H3 from the X axis. The intersection of the distance H3 and the width W1 intersects the circumference of the radius R2max, but is not limited thereto. The straight line portion 612S forming the square lower surface is parallel to the X axis. The balancer-side weight 612A has the same shape as that of fig. 4 shown in embodiment 1. The scroll compressor 100 provided with the crankshaft 6 having the balancer portion 61B has the same effects as those of embodiment 1.

Next, the 1 st and 2 nd sides of the counter balance weight 612B according to embodiment 3 are described with reference to fig. 16.

First, the 1 st side is a side (straight line portion) formed in either or both of the 3 rd and 4 th quadrants of the coordinate system in the balancer opposing side weight portion. The 2 nd side is a side (straight line portion) connected to the 1 st side of the balancer portion 61B in a coordinate system of a plane perpendicular to the rotation axis of the crankshaft. The relationship between the 1 st side and the 2 nd side is the same in the following embodiments, and therefore, the description thereof is appropriately omitted.

As shown in fig. 16, the straight portions 612S of the counter balance weight 612B are respectively defined as sides S11, S12, and S13. Thus, any of the sides S11, S12, and S13 corresponds to the 1 st side formed in either or both of the 3 rd and 4 th quadrants of the coordinate system in the counter balance weight 612B. When the side S11 is the 1 st side, the side S12 corresponds to the 2 nd side which is the side connected to the side S11.

When the side S12 is the 1 st side, the sides S12 and S13 are equal to the side connected to the side S12, that is, the 2 nd side. The side S11 is formed in quadrant 4 of the X-Y coordinate system and is formed parallel to the Y axis. The side S12 is formed continuously in both the 3 rd and 4 th quadrants of the X-Y coordinate system and is formed parallel to the X axis. The side S13 is formed in quadrant 3 of the X-Y coordinate system and is formed parallel to the Y axis.

By providing the side S12 parallel to the X axis in this way, it is possible to perform machining by a general-purpose machine such as a 2-axis lathe simultaneously with other parts of the crankshaft 6. Further, since machining can be performed simultaneously, control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved. Further, since the processing can be performed by general-purpose machines, the equipment investment is small, and the manufacturing cost can be reduced.

The counter balance weight 612B is formed in a shape having sides S11 and S13 having a distance H3 from the X axis in the X-Y coordinate system. Therefore, the following effects are achieved: the weight of the counter balance weight 612B can be reduced without significantly impairing the rigidity of the crankshaft 6, the weight 612 can be made smaller, and a larger centrifugal force can be eliminated. Further, since the cutting tool is a straight line, the cutting tool can be easily machined by an end mill or the like.

In the case of the shape shown in fig. 16, the sides S11, S12, and S13 can be formed by cutting from the state shown in fig. 7B of embodiment 2.

According to the scroll compressor of embodiment 3 configured as described above, the same effects as those of the above embodiments are achieved, and,

in a coordinate system in a plane perpendicular to the rotation axis of the crankshaft,

the balancer portion has a 2 nd side connected to the 1 st side,

Furthermore, according to the scroll compressor of embodiment 3,

the balancer-side weight portion has a semicircular shape centered on the origin,

the balancer opposite side weight portion is formed in a polygonal shape,

Furthermore, according to the scroll compressor of embodiment 3,

at the maximum distance of the semicircle provided with the balancer-side weight portion is R1max,

when the maximum distance in the X-axis direction of the balancer counter weight is W1,

is formed in a relationship of R1max > W1,

therefore, the relationship of the area of the balancer-side weight portion > the area of the balancer-opposite-side weight portion can be obtained more simply and reliably.

Embodiment 4.

Next, a crankshaft 6 according to embodiment 4 will be described with reference to the drawings. Fig. 10A is a side view of the crankshaft of embodiment 4, and fig. 10B is a plan view of the crankshaft of embodiment 4 as viewed from the U side (arrow Z) of fig. 10A. In addition, fig. 11A shows an enlarged view of the balancer portion 61B of fig. 10A, and fig. 11B shows a sectional projection view of the line A-A of fig. 11A. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 11, the balancer-side weight 612A and the balancer-opposite-side weight 612B are integrally formed in a substantially inverted convex shape. The balancer-side weight 612A has a substantially mushroom-like shape: which has an arc of radius R1max, forms a width W1 parallel to the X axis up to a position at a prescribed distance H1 from the X axis, and the balancer opposing weight portion 612B has the following shape: the W1 is extended to a position at a distance H2 from the X-axis, and a straight line having a width W2 at a prescribed distance H3 from the X-axis and parallel to the X-axis is connected to the W1 at the position at the distance H2 by a diagonal line.

In the substantially mushroom shape, a straight portion 612S is provided on the balancer opposing side weight portion 612B side. Referring to fig. 17 described later, the intersection point of the side S18 and the side S17, the intersection point of the side S17 and the side S16, the intersection point of the side S16 and the side S15, and the intersection point of the side S15 and the side S14 intersect the circumference of the radius R2max shown in fig. 11B, but is not limited thereto. The scroll compressor 100 provided with the crankshaft 6 having the balancer portion 61B has the same effects as those of embodiment 1.

Next, the 1 st and 2 nd sides of embodiment 4 will be described with reference to fig. 17. In the figure, the sides S14, S15, S16, S17, S18, V11, and V14 are respectively defined. Thus, any of the sides S14, S15, S16, S17, and S18 corresponds to the 1 st side formed in either or both of the 3 rd and 4 th quadrants of the coordinate system in the counter balance weight 612B. The sides V11 and V14 correspond to the 2 nd side connected to the 1 st side.

When the side S16 is the 1 st side, the sides S15 and S17 correspond to the 2 nd side which is the side connected to the side S16. When the side S14 is the 1 st side, the sides S15 and V11 correspond to the 2 nd side which is the side connected to the side S14. When the side S18 is the 1 st side, the sides S17 and V14 correspond to the 2 nd side which is the side connected to the side S18. When the side S15 is the 1 st side, the sides S14 and S16 correspond to the 2 nd side which is the side connected to the side S15. When the side S17 is the 1 st side, the sides S18 and S16 correspond to the 2 nd side which is the side connected to the side S17.

The side S14 is formed continuously in both the 1 st quadrant and the 4 th quadrant of the X-Y coordinate system, and is formed parallel to the Y axis. Side S15 is formed in quadrant 4 of the X-Y coordinate system.

The side S16 is formed continuously in both the 3 rd and 4 th quadrants of the X-Y coordinate system and is formed parallel to the X axis. Side S17 is formed in quadrant 3 of the X-Y coordinate system. The side S18 is formed continuously in both the 2 nd and 3 rd quadrants of the X-Y coordinate system and is formed parallel to the Y axis. The side V11 is formed in quadrant 1 of the X-Y coordinate system, intersecting perpendicularly with the side S14. However, it is not limited to being vertical. Side V14 is formed in quadrant 2 of the X-Y coordinate system, intersecting perpendicularly with side S18. However, it is not limited to being vertical.

Further, the counter balance weight 612B has a shape in which the width W1 is extended to a position at a distance H2 from the X axis, and a straight line having the width W2 at a position at a predetermined distance H3 from the X axis and being parallel to the X axis is connected to the width W1 at a position at the distance H2 by a diagonal line, whereby the weight of the counter balance weight 612B can be reduced, and the weight 612 can be miniaturized. Further, greater cancellation is enabled.

The balancer-opposite-side weight portion 612B is formed in an X-Y coordinate system so as to include: (part of) the side S14 and (part of) the side S18, which are straight line portions 612S having a length of the distance H2 from the X axis; and (a part of) side S14 and (a part of) side S18, which are straight portions 612S having a width W1. Therefore, the following effects are achieved: the weight of the counter balance weight 612B can be further reduced without significantly impairing the rigidity of the crankshaft 6, the weight 612 can be further reduced in size, and a larger centrifugal force can be eliminated. Further, since the cutting tool is a straight line, machining can be easily performed by a cutting tool such as an end mill.

The balancer-opposite-side weight portion 612B is formed in an X-Y coordinate system so as to include: (part of) side S14 and (part of) side S18, which have a distance H2; and a side S15 or a side S17 connected to the side S14 or the side S18, and a side S16 parallel to the X axis. Therefore, the following effects are achieved: the weight of the counter balance weight 612B can be further reduced without significantly impairing the rigidity of the crankshaft 6, the weight 612 can be further reduced in size, and a larger centrifugal force can be eliminated.

In the case of the shape shown in fig. 17, the sides S14 to S18 are straight lines, and therefore, the effect of enabling easy machining by a cutting tool such as an end mill from the state shown in fig. 7B of embodiment 2 described above is obtained. It is preferable that the distance H1 and the distance H2 are set to the same length. By setting the distance h1=h2, it is possible to perform machining by a general-purpose machine such as a 2-axis lathe simultaneously with other parts of the crankshaft 6. Since machining can be performed simultaneously, control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll 32 can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved. Further, since the processing can be performed by general-purpose machines, the investment is small and the manufacturing cost can be reduced.

Here, the 1 st and 2 nd sides, and still other examples will be described with reference to fig. 18, 25, and 26. Fig. 18 and 26 show only the shape on the plane of the balancer portion 61B in the X-Y coordinate system, as in the above embodiments, but are omitted from other parts. Fig. 25 is a cross-sectional view showing a structure of a member before forming the balancer parts 61B in the X-Y coordinate system, as in the above embodiments, and only shows a planar shape.

First, in the case of obtaining the balancer portion 61B shown in fig. 18 and 26, the balancer portion 61B of the present application is manufactured by cutting from a columnar member formed by columnar forging or casting, for example. Thus, as shown in fig. 25, the shape of the circle 600 in the X-Y coordinate system is obtained before the cutting process. The balancer portion 61B is formed by cutting from the circular shape 600.

In fig. 18A, a side S19 that is the 1 st side continuing in the 3 rd and 4 th quadrants is formed at the balancer opposite side weight 612B. Further, the example is that the 2 nd side connected to the 1 st side is not formed. Fig. 18B is an example in which the 1 st and 2 nd sides are not formed. In the balancer-side weight 612A, a side V15 is formed in quadrant 1, and a side V16 is formed in quadrant 2.

In fig. 18C, a side S20 is formed as the 1 st side in the 4 th quadrant of the balancer opposing weight 612B. A side connected to the side S20 is formed as a side V17 in quadrant 1 of the balancer-side weight 612A. Thus, the side V17 corresponds to the 2 nd side. In fig. 18D, a side S21 as the 1 st side is continuously formed from the 4 th quadrant of the balancer opposing side weight 612B to the balancer side weight 612A.

In fig. 26A, a side S24 as a 1 st side is formed continuously in the 3 rd and 4 th quadrants of the balancer opposing side weight 612B. Further, the example is that the 2 nd side connected to the 1 st side is not formed. In fig. 26B, a side S25 as a 1 st side is formed in a 3 rd quadrant of the balancer opposing weight portion 612B, and a side S26 as a 1 st side is formed in a 4 th quadrant. Further, the example is that the 2 nd side connected to the 1 st side is not formed.

In fig. 26C, a side S27 is formed in the 3 rd quadrant of the balancer opposing weight portion 612B, and a side S27 is formed in the 4 th quadrant. Thus, any one of the sides S26 and S25 corresponds to the 1 st side formed in either or both of the 3 rd and 4 th quadrants of the coordinate system in the counter balance weight 612B. When the side S27 is the 1 st side, the side S28 corresponds to the 2 nd side which is the side connected to the side S27. When the side S28 is the 1 st side, the side S27 corresponds to the 2 nd side which is the side connected to the side S28.

In fig. 26D, sides S29, S30, and S31 are formed in the counter balance weight 612B. Thus, any of the sides S29, S30, and S31 corresponds to the 1 st side formed in either or both of the 3 rd and 4 th quadrants of the coordinate system in the counter balance weight 612B. When the side S29 is the 1 st side, the side S30 corresponds to the 2 nd side which is the side connected to the side S29.

When the 1 st side is the side S30, the sides S29 and S31 are the same as the 2 nd side which is the side connected to the side S30. When the side S31 is the 1 st side, the side S30 corresponds to the 2 nd side which is the side connected to the side S31. The side S31 is formed in quadrant 4 of the X-Y coordinate system. The side S30 is formed continuously in both the 3 rd and 4 th quadrants of the X-Y coordinate system and is formed parallel to the X axis. Side S29 is formed in quadrant 3 of the X-Y coordinate system.

As described above, the areas of the balancer-side weight 612A and the counter-balancer-side weight 612B of the balancer section 61B in the X-Y coordinate system are only required to have

The relationship of the area of the balancer-side weight 612A > the area of the balancer-opposite-side weight 612B,

various examples can be considered regarding the formation of the 1 st side and the side connected to the 1 st side, i.e., the 2 nd side, of the balancer opposing side weight portion 612B.

Further, since the balancer opposing side weight portion 612B is formed in a polygon including the 1 st side and the 2 nd side, the 1 st side and the 2 nd side can be manufactured simultaneously with 1 tool by making the sides perpendicular or parallel to each other, and thus control of the center of gravity position becomes easy. Therefore, the centrifugal force of the orbiting scroll can be offset with high accuracy, and therefore, the vibration is small, and the reliability can be improved.

According to the scroll compressor of embodiment 4 configured as described above, the same effects as those of the above embodiments are achieved, and,

the balancer-side weight portion is formed in a mushroom shape having a semicircle shape centering on the origin and a polygon connected to the semicircle shape,

the balancer opposite side weight portion is formed in an inverted convex shape connected to the polygon,

Furthermore, according to the scroll compressor of embodiment 4,

when the maximum distance of the semicircle of the balancer-side weight is R1max and the maximum distance of the X-axis direction of the balancer-opposite-side weight is W1,

is formed in a relationship of R1max > W1,

Embodiment 5.

Next, a crankshaft 6 according to embodiment 5 will be described with reference to the drawings. Fig. 12A is a side view of the crankshaft of embodiment 5, and fig. 12B is a plan view of the crankshaft of embodiment 5 as viewed from the U side (arrow Z) of fig. 12A. In addition, fig. 13A shows an enlarged view of the balancer portion 61B of fig. 12A, and fig. 13B shows a sectional projection view of the line A-A of fig. 12A. Fig. 14A is a side view of another crankshaft according to embodiment 5, and fig. 14B is a sectional view of the crankshaft shown in fig. 14A taken along line A-A. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 13, the balancer-side weight 612A is the same as that of fig. 4 of embodiment 1 described above. The balancer opposing counterweight 612B has the same planar shape as that of fig. 9B of embodiment 3 described above, and has a cut-in portion 612K as a recess portion provided in the direction of the rotation axis 6CL within the range of the width WL1 at a position axially distant from the end face width WL2 of the main bearing portion 61A by a predetermined distance H4 to the distance H3. Although the distance H4 is the same size as d/4, it is not limited thereto.

Instead of the cut-in portion 612K, a drilled hole 612R having a predetermined diameter DR as a recess may be provided in the counter weight portion 612B on the counter weight side as shown in fig. 14A and 14B. Although the depth of the borehole 612R is set to reach the d/4 position, it is not limited thereto. The scroll compressor 100 provided with the crankshaft 6 having the balancer portion 61B has the same effects as those of embodiment 1. In embodiment 5, the drilled hole 612R is a blind hole formed by an end mill, and the shape of the hole and the machining method are not limited.

According to the scroll compressor of embodiment 5 configured as described above, the same effects as those of the above embodiments are achieved, and,

the balancer opposite side weight portion is formed with a recess,

therefore, the weight portion can be made lightweight.

Furthermore, according to the scroll compressor of embodiment 5,

further, since the balancer-opposite-side weight portion is provided with a cutout portion having a predetermined width WL1 in the axial direction of the crankshaft and extending from a predetermined distance H4 to a predetermined distance H3 from the X axis, the recess can be easily obtained by the cutout portion.

Furthermore, according to the scroll compressor of embodiment 5,

Since the hole of a predetermined diameter is further provided in the Y-axis of the polygonal portion of the counterweight on the opposite side of the balancer, the recess can be easily obtained by the hole.

Embodiment 6.

Next, embodiment 6 will be described. The purpose of embodiment 6 is to improve the flow of refrigerant in the middle housing 11 shown in fig. 2, thereby further improving the efficiency of the scroll compressor 100. When the clearance between the tip of the 1 st scroll 312 of the fixed scroll 31 of the compression driving unit 3 shown in fig. 2 and the surface of the 1 st base plate 321 of the orbiting scroll 32 provided with the 2 nd scroll 322 is Q, a method of adjusting the clearance Q will be described with reference to fig. 15. Fig. 15 is an enlarged partial cross-sectional view of the compression driving unit 3 of fig. 2. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

When the dimensions of the respective portions are set as described below, the gap Q between the tip of the 1 st scroll 312 of the fixed scroll 31 and the 1-end side surface UA of the 2 nd base plate 321 of the orbiting scroll 32 can be expressed by the following equation.

L＝M+Q+N+T+P

Thus, the first and second substrates are bonded together,

Q＝L-M-N-T-P

here the number of the elements to be processed is,

l: distance between the 1 st positioning surface 113 of the middle housing 11 and the 2 nd positioning surface 116 of the middle housing 11

M: distance between 1 st positioning surface 113 of middle housing 11 and tooth tip of 1 st scroll 312 of fixed scroll 31

N: thickness of 2 nd base 321 of orbiting scroll 32

T: thickness of thrust plate 24

P: distance between the 2 nd positioning surface 116 of the middle housing 11 and the flat surface 212 of the 1 st frame 2

Here, when the dimensions of the respective portions are known by measurement, a desired gap Q can be set by adjusting the thickness T of the thrust plate 24 that can be produced in a plurality of kinds of mass production. Further, by adjusting the gap Q, leakage of the refrigerant into the compression space through the gap Q can be suppressed, and therefore, loss of the scroll compressor 100 can be reduced.

According to the scroll compressor of embodiment 6 configured as described above, the same effects as those of the above embodiments are achieved, and,

a thrust plate is arranged between the 1 st frame of the compression driving part and the 2 nd base plate of the swing vortex piece,

therefore, leakage of the refrigerant introduced into the scroll compressor can be suppressed.

Embodiment 7.

Next, embodiment 7 will be described. Fig. 19A is a side view of the crankshaft of embodiment 7, and fig. 19B is a sectional view of the crankshaft shown in fig. 19A taken along line A-A. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted. As shown in fig. 19, a QR code (registered trademark) or the like may be provided as the marker 201 of the individual discriminating unit for discriminating an individual in the straight line portion 612S of the counter balance portion 612B.

When there is no flat portion or almost no flat portion in the crankshaft and the curvature of the curved portion is small, it is difficult to provide an individual discriminating portion for performing individual discrimination. However, in the present application, since the straight portion 612S of the balancer opposing weight portion 612B is provided, the individual management can be performed by providing the marker portion 201 for discriminating the individual such as a QR code (registered trademark), and the reduction of the defective rate and the high functionality of the compressor such as the combination sorting can be achieved.

In the present embodiment, the marking portion 201 is provided on the straight portion 612S of the counter balance weight portion 612B, but may be provided on the outer peripheral side of the radius R1max of the counter balance weight portion 612A. By integrally forming the balancer-side weight portion 612A and the crankshaft 6 from the same forming material without a seam, the balancer-side weight portion 612A has a larger radius than a normal crankshaft, and thus has a smaller curvature, and by providing the individual discriminating portion, the individual management can be performed, and the scroll compressor 100 can be reduced in defective rate and increased in functionality such as combination sorting, as compared with a normal case.

According to the scroll compressor of embodiment 7 configured as described above, the same effects as those of the above embodiments are achieved, and,

The balancer unit is provided with an individual discriminating unit,

therefore, individual management is possible, and the scroll compressor 100 can be reduced in defective rate and increased in functionality such as combination sorting.

Embodiment 8.

Next, embodiment 8 will be described. Fig. 20A is a side view of the crankshaft of embodiment 8, and fig. 20B is a top view of the crankshaft of embodiment 8. Fig. 21 is a cross-sectional view of the scroll compressor according to embodiment 8. Fig. 22 is a partial cross-sectional view of the scroll compressor according to embodiment 8. Fig. 23 is a partial cross-sectional view of another scroll compressor of embodiment 8. In the drawings, the same portions as those of the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

As shown in fig. 20 to 22, the balancer housing 301 is fixed to the U-side end surface of the balancer section 61B of the crankshaft 6 through the fixing hole 302 of the bolt or the like and the bolt 303 or the like, instead of being fixed to the 1 st frame 2. The balancer housing 301 is attached to the fixing hole 302 provided in the U-side end surface of the balancer section 61B of the crankshaft 6 by bolts 303, instead of being attached to the 1 st frame 2.

By integrating the balancer housing 301 with the crankshaft 6 instead of the 1 st frame 2, the fear that the balancer section 61B is deformed by rotation and contacts the balancer housing 301 is eliminated. Therefore, the diameter of the balancer section 61B can be increased. Accordingly, the rotational speed of the scroll compressor 100 can be increased in response to the larger centrifugal force of the orbiting scroll 32, and the scroll can be increased to increase the compression amount of the scroll compressor 100.

As shown in fig. 20B, the hole 302 is preferably formed in the vicinity of the outer periphery of the balancer weight 612A. By providing the balancer-side weight portion 612A, the centrifugal force of the orbiting scroll can be further eliminated in accordance with the weight of the bolt 303.

As another example, as shown in fig. 23, in order to fix the balancer housing 301 to the balancer section 61B, a hole 302 for fixing a bolt or the like and a bolt 303 may be provided on the outer peripheral portion of the balancer-side weight section 612A with a radius R1 max. Since the position of the bolt 303 is farther than the position of the rotation shaft 6CL, the centrifugal force of the orbiting scroll can be further eliminated. Further, the weight 304 may be provided when the bolt 303 is fastened to the hole 302. In order to prevent loosening, an adhesive is preferably used when fastening the bolt 303.

According to the scroll compressor of embodiment 8 configured as described above, the same effects as those of the above embodiments are achieved, and,

a balancer housing is fixedly provided in the balancer section,

therefore, by integrating the balancer housing with the balancer housing, the fear that the balancer housing is deformed by rotation and comes into contact with the balancer housing is eliminated.

While various illustrative embodiments and examples have been described herein, the various features, aspects, and functions described in one or more embodiments are not limited to the application of the particular embodiments, and may be applied to the embodiments alone or in various combinations.

Accordingly, numerous modifications not illustrated can be envisaged within the scope of the technology disclosed in the present application. For example, the case where at least 1 component is deformed, added or omitted, or the case where at least 1 component is extracted and combined with the components of other embodiments is included.

Description of the reference numerals

1: a housing; 100: a scroll compressor; 11: a middle shell; 113: a 1 st positioning surface; 116: a 2 nd positioning surface; 12: an upper housing; 13: a lower housing; 15: a discharge pipe; 2: a 1 st frame; 212: a flat surface; 22: a bearing part; 24: a thrust plate; 2A: a bearing part; 3: a compression driving part; 301: a balancer housing; 302: a hole; 303: a bolt; 304: a counterweight; 31: a fixed scroll; 312: a 1 st scroll; 32: a swinging scroll; 321: a 2 nd substrate; 322: a 2 nd scroll; 34: a compression chamber; 4: a driving section; 4A: a rotor; 5: a 2 nd frame; 5A: a sub-bearing portion; 6: a crankshaft; 60: an oil passage; 61: a main shaft portion; 611: a flange portion; 612: a weight part; 612A: a balancer-side weight portion; 612B: a balancer counter weight portion; 612BB: an oval shape; 612K: a cut-in portion; 612R: drilling holes; 612S: a straight line portion; 61A: a main bearing portion; 61B: a balancer section; 61C: a rotor hot press fit portion; 61D: a sub-bearing portion; 61G: the 1 st center of gravity; 62: an eccentric shaft portion; 62C: a 2 nd center of gravity; 62CL: an eccentric shaft; 65: a sleeve bearing; 66: a balancer; 6CL: a rotation shaft; q: a gap.

Claims

1. A scroll compressor, wherein the scroll compressor comprises: a crankshaft supported by a bearing fixed to the housing; a drive unit for the crankshaft; a swing scroll provided on an eccentric shaft portion of the crankshaft; and a fixed scroll provided in the housing, wherein a balancer portion is provided in a main shaft portion of the crankshaft, and the balancer portion reduces unbalanced force accompanying rotation of the crankshaft, and is formed as a single body.

2. The scroll compressor of claim 1, wherein,

in order to form a relationship in which the weight of the balancer-side weight portion > the weight of the balancer-opposite-side weight portion,

the area in at least 1 or more sections perpendicular to the rotation axis has

The area of the balancer-side weight > the area of the balancer-opposite-side weight.

3. The scroll compressor of claim 2, wherein,

in a coordinate system of a plane perpendicular to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is set as an X axis, a longitudinal center line of the crankshaft perpendicular to the X axis is set as a Y axis, and a point on the rotation axis where the X axis intersects the Y axis is defined as an origin,

The balancer opposite side weight has a 1 st side in either or both of the 3 rd and 4 th quadrants of the coordinate system.

4. The scroll compressor of claim 3, wherein,

the balancer section has a 2 nd side connected to the 1 st side.

5. The scroll compressor of any one of claims 2 to 4, wherein,

A relationship that a maximum distance of the balancer-side weight portion > a maximum distance of the balancer-opposite-side weight portion is formed.

6. The scroll compressor of any one of claims 2 to 5, wherein,

A part of the outer shape of the counterweight part on the opposite side of the balancer is formed in an elliptical shape or a concave-convex shape.

7. The scroll compressor of any one of claims 2 to 6, wherein,

with the origin point as the center of the device,

an angle formed by a line passing through the 1 st gravity center of the balancer-side weight and the origin and a line passing through the 2 nd gravity center of the balancer-opposite-side weight and the origin is 90 degrees or more and 270 degrees or less.

8. The scroll compressor of claim 3, 4 or 7, wherein,

the balancer opposite side weight portion is formed in a polygonal shape.

9. The scroll compressor of claim 3, 4 or 7, wherein,

The balancer opposite side weight portion is formed in an inverted convex shape connected to the polygon.

10. The scroll compressor of claim 8 or 9, wherein,

the relationship R1max > W1 is formed.

11. The scroll compressor of any one of claims 2 to 10, wherein,

the balancer opposite side weight portion is formed with a recess.

12. The scroll compressor of any one of claims 2 to 11, wherein,

the balancer portion is provided with a flange portion that is connected to the balancer-side weight portion in the axial direction.

13. The scroll compressor of any one of claims 1 to 12, wherein,

a thrust plate is provided between the 1 st frame of the compression driving section and the 2 nd base plate of the orbiting scroll.

14. The scroll compressor of any one of claims 1 to 13, wherein,

the balancer unit is provided with an individual discriminating unit.

15. The scroll compressor of any one of claims 1 to 14, wherein,

a balancer housing is fixedly provided in the balancer section.