JP7442668B2 - scroll compressor - Google Patents

Description

The present application relates to a scroll compressor.

A balance weight may be attached to the crankshaft of a scroll compressor to balance the centrifugal force and moment generated around the shaft. One example is a balance weight that has a rotating shaft and an annular outer circumferential surface, is fixed to the rotating shaft and rotates together with the rotating shaft, and a part of the outer circumferential surface is provided with a balance weight for adjusting the angular position of the balance weight with respect to the rotating shaft. A technique is disclosed in which deflection of a rotating shaft is suppressed using a balance weight in a configuration in which a recess is formed (for example, see Patent Document 1).

Japanese Patent Application Publication No. 2016-50551

However, the technique disclosed in Patent Document 1 selects a balance weight that corresponds to the rotating shaft, adjusts the angle of the balance weight, and attaches the balance weight to the rotating shaft, and there is a risk of attaching the wrong balance weight. There is a risk of angular misalignment when installing the balance weight, and in order to prevent this, sophisticated assembly equipment, jigs, and complicated assembly work are required. However, since shrink fitting is used, there are problems such as requiring advanced processing and providing a ring portion for shrink fitting, which increases the size of the balance weight.

The present application discloses a technique for solving the above problems, and aims to provide a small-sized scroll compressor that is easy to assemble.

The scroll compressor disclosed in the present application includes a crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft section of the crankshaft, and a scroll compressor for the shell. a fixed scroll provided in the crankshaft, and a balancer part formed in one piece is provided on the main shaft part of the crankshaft to reduce unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Since the weight of the balancer side weight part>the weight of the anti-balancer side weight part holds,
The area of at least one cross section perpendicular to the rotation axis is
having a relationship of area of the balancer side weight part>area of the anti-balancer side weight part,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
The anti-balancer side weight portion is formed from the first side toward the origin.
Furthermore, the scroll compressor disclosed in this application is
A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have the relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
Coordinates in a plane perpendicular to the rotation axis of the crankshaft,
The balancer section has a second side that is continuous with the first side.
Furthermore, the scroll compressor disclosed in this application is
A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have a relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
The balancer side weight part and the anti-balancer side weight part have a semicircular shape centered on the origin, and the maximum distance of the semicircle from the origin is:
Maximum distance of the weight part on the balancer side > Maximum distance of the weight part on the anti-balancer side
It was formed based on the relationship between
Furthermore, the scroll compressor disclosed in this application is
A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have a relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either the third quadrant or the fourth quadrant of the coordinates, or both;
The balancer side weight part has a semicircular shape centered on the origin,
The anti-balancer side weight portion is formed in a polygonal shape.
Furthermore, the scroll compressor disclosed in this application includes:
A crankshaft supported by a bearing fixed to a shell, a driving section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section includes a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including a rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have a relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either the third quadrant or the fourth quadrant of the coordinates, or both;
The balancer side weight part is formed in a mushroom shape having a semicircular shape centered on the origin and a polygonal shape connected to the semicircular shape,
The anti-balancer side weight portion is formed in an inversely convex shape that is continuous with the polygonal shape.
Furthermore, the scroll compressor disclosed in this application includes:
A crankshaft supported by a bearing fixed to a shell, a driving section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section includes a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including a rotation axis of the crankshaft, and
Since the weight of the balancer side weight part>the weight of the anti-balancer side weight part holds,
The area of at least one cross section perpendicular to the rotation axis is
having a relationship of area of the balancer side weight part>area of the anti-balancer side weight part,
The balancer section is provided with a collar section that is connected to the balancer side weight section in the axial direction.

Since the scroll compressor disclosed in the present application employs the above-described configuration, it has the advantage of being easy to assemble and providing a small-sized scroll compressor.

1 is a perspective view of a scroll compressor according to Embodiment 1. FIG. 1 is a sectional view of a scroll compressor according to Embodiment 1. FIG. 3A is a side view of the crankshaft according to the first embodiment, and FIG. 3B is a top view of the crankshaft according to the first embodiment. 4A is a side view of the crankshaft according to the first embodiment, and FIG. 4B is a cross-sectional projection view taken along the line AA of the crankshaft shown in FIG. 4A. 5A is a side view of another crankshaft according to the first embodiment, and FIG. 5B is a cross-sectional projection view taken along the line AA of the other crankshaft shown in FIG. 5A. 6A is a side view of the crankshaft according to the second embodiment, and FIG. 6B is a top view of the crankshaft according to the second embodiment. 7A is a side view of the crankshaft according to the second embodiment, and FIG. 7B is a cross-sectional projection view taken along line AA of the crankshaft shown in FIG. 7A. 8A is a side view of the crankshaft according to the third embodiment, and FIG. 8B is a top view of the crankshaft according to the third embodiment. 9A is a side view of the crankshaft according to the third embodiment, and FIG. 9B is a cross-sectional projection view taken along the line AA of the crankshaft shown in FIG. 9A. 10A is a side view of the crankshaft according to the fourth embodiment, and FIG. 10B is a top view of the crankshaft according to the fourth embodiment. FIG. 11A is a side view of the crankshaft according to the fourth embodiment, and FIG. 11B is a cross-sectional projection view taken along the line AA of the crankshaft shown in FIG. 11A. 12A is a side view of the crankshaft according to the fifth embodiment, and FIG. 12B is a top view of the crankshaft according to the third embodiment. 13A is a side view of the crankshaft according to the fifth embodiment, and FIG. 13B is a cross-sectional projection view taken along the line AA of the crankshaft shown in FIG. 13A. 14A is a side view of another crankshaft according to Embodiment 5, and FIG. 14B is a sectional projection view taken along the line AA of the crankshaft shown in FIG. 14A. FIG. 7 is a partially enlarged view of a compression drive section of a scroll compressor according to a sixth embodiment. 9A is a diagram showing the configuration of the balancer section in the XY coordinates of FIG. 9A. FIG. FIG. 11A is a diagram showing the configuration of the balancer section in the XY coordinates of FIG. 11A. FIG. 18A is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment, FIG. 18B is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment, and FIG. 18C is a diagram showing the other configuration of the balancer unit in the XY coordinate according to the fourth embodiment. FIG. 18D is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment. FIG. 18D is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment. 19A is a side view of the crankshaft according to the seventh embodiment, and FIG. 19B is a cross-sectional projection view taken along line AA of the crankshaft shown in FIG. 19A. 20A is a side view of the crankshaft according to the eighth embodiment, and FIG. 20B is a top view of the crankshaft according to the eighth embodiment. FIG. 7 is a sectional view of a scroll compressor according to an eighth embodiment. FIG. 7 is a partial cross-sectional view of a scroll compressor according to an eighth embodiment. FIG. 7 is a partial cross-sectional view of another scroll compressor according to Embodiment 8. FIG. 3 is a diagram showing another configuration of the balancer section in the XY coordinates of the scroll compressor according to the first embodiment. FIG. 7 is a cross-sectional view showing the shape of a member before forming a balancer portion of a scroll compressor according to a fourth embodiment. 26A is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment, FIG. 26B is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment, and FIG. 26C is a diagram showing the other configuration of the balancer unit in the XY coordinate according to the fourth embodiment. FIG. 26D is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment. FIG. 26D is a diagram showing another configuration of the balancer unit in the XY coordinate according to the fourth embodiment.

Embodiment 1.
Embodiment 1 will be described based on the drawings. FIG. 1 is a perspective view of a vertical scroll compressor 100. FIG. 2 is a sectional view of the vertical scroll compressor 100, with the U side indicating the upper side and the L side indicating the lower side. Note that in other figures, the U side and L side refer to the U side and L side in FIG. 2. Furthermore, since the relationship is the same in the following embodiments, the explanation thereof will be omitted as appropriate.

As shown in FIGS. 1 and 2, the scroll compressor 100 includes a shell 1 consisting of a middle shell 11, an upper shell 12, and a lower shell 13 as main components, a crankshaft 6 supported by a bearing of the middle shell 11, and a crankshaft 6 supported by a bearing of the middle shell 11. It includes a drive section 4 that rotationally drives a shaft 6, and a compression drive section 3 provided with a fixed scroll 31 and an oscillating scroll 32.

An outline of the operation of the scroll compressor 100 having such a configuration will be explained. The crankshaft 6 is rotated by the operation of the drive unit 4, and the refrigerant flows into the compression drive unit 3 through the first frame 2. Here, the oscillating scroll 32 provided on the eccentric shaft portion 62 of the crankshaft 6 oscillates, and the refrigerant is compressed within the compression chamber 34 . The compressed refrigerant flows into the discharge pipe 15 via the fixed scroll 31.

Note that a balancer cover 301 is installed in a balancer section 61B, which will be described later, and is provided between the first frame 2 and the main shaft section 61, which are arranged on the L side of the swinging scroll 32. The balancer cover 301 retains refrigerating machine oil that has risen inside the scroll compressor 100 along with the refrigerant through an oil passage 60 (described later), suppresses taking out of the refrigerating machine oil to the outside of the scroll compressor 100, and prevents the scroll compressor 100 from moving out. It has a function of suppressing a decrease in the heat exchange capacity of the heat exchanger connected to the heat exchanger 100. The balancer cover 301 is fixed and installed on the first frame 2 with bolts or the like.

3A and 3B show a crankshaft 6 equipped with a balancer part 61B formed as an integral part for reducing the unbalanced force accompanying the rotation of the crankshaft 6, which is the gist of the present application. 3A is a side view of the crankshaft according to the first embodiment, and FIG. 3B is a top view of the crankshaft according to the first embodiment as seen from the U side (arrow Z) direction of FIG. 3A. Note that FIG. 4A shows an enlarged view of the balancer portion 61B in FIG. 3A, and FIG. 4B shows a cross-sectional projection view taken along the line AA in FIG. 4A.

In addition, as shown in FIG. 4, in coordinates in a plane perpendicular to the rotation axis 6CL of the crankshaft 6, a line on a horizontal plane including the rotation axis 6CL is defined as the X axis, and a vertical center line of the crankshaft 6 perpendicular to the X axis. is defined as the Y-axis, and the point on the rotation axis 6CL where the X-axis and the Y-axis intersect is defined as the origin C. Moreover, the balancer part 61B has a balancer side weight part 612A and an anti-balancer side weight part 612B as a weight part 612, and is connected to a plane including the rotation axis 6CL of the crankshaft 6. A side weight portion 612B is provided.

The balancer side weight portion 612A is formed in the first and second quadrants in the XY coordinate defined above, and the anti-balancer side weight portion 612B is formed in the third and fourth quadrants. In the first embodiment and other embodiments, the relationship between the X axis, the Y axis, the origin C, the crankshaft 6 and the rotating shaft 6CL, the balancer side weight part 612A, and the anti-balancer side weight part 612B is Since the relationships are the same, the description of the relationships will be omitted as appropriate. Further, the first quadrant, the second quadrant, the third quadrant, and the fourth quadrant are illustrated only in FIG. 4B, and their description is omitted in other similar figures.

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 is arranged so that the rotating shaft 6CL coincides with the axis center line of the middle shell 11 shown in FIG. The eccentric shaft portion 62 is provided on the U side of the crankshaft 6, with the eccentric shaft 62CL being eccentric with respect to the rotating shaft 6CL of the main shaft portion 61.

The oil passage 60 is provided to penetrate the crankshaft 6 from the L side end to the U side end. In FIG. 3A, the oil passage 60 is provided along the rotation axis 6CL of the crankshaft 6, but the oil passage 60 is not limited to this and may be provided below the X axis in FIG. 4B.

The main shaft portion 61 is provided with a main bearing portion 61A, a balancer portion 61B, a rotor shrink-fit portion 61C, and a sub-bearing portion 61D in order from the U side. The rotor 4A of the drive unit 4 shown in FIG. 2 is provided in the rotor shrink-fitting portion 61C. The main bearing portion 61A is inserted into the bearing portion 2A of the first frame 2. The sub-bearing portion 61D is inserted into the sub-bearing portion 5A of the second frame 5. Note that, as shown in FIG. 2, a sleeve bearing 65 that is driven by rotation of the crankshaft 6 is provided between the bearing portion 2A of the first frame 2 and the main bearing portion 61A of the crankshaft 6.

As shown in FIG. 4B, in the weight part 612 forming the balancer part 61B, a smooth semicircular balancer side weight part 612A with a radius R1max extends over the first and second quadrants of the XY coordinates, and the third A smooth semicircular anti-balancer side weight portion 612B with a radius R2max is provided across the quadrant and the fourth quadrant. That is, a balancer side weight section 612A and an anti-balancer side weight section 612B are provided connected to the Y axis. By setting the radius R1max>radius R2max, the balancer side weight portion 612A and the anti-balancer side weight portion 612B are distinguished. That is, based on the magnitude relationship between the weight and the position of the center of gravity, they are the balancer side weight portion 612A and the anti-balancer side weight portion 612B. In addition, when configured as shown in FIG. 4, the radius R1max is the maximum distance from the origin C of the balancer side weight part 612A, and the radius R2max is the maximum distance from the origin C of the anti-balancer side weight part 612B. Become.

Here, the first center of gravity 61G of the balancer side weight section 612A and the second center of gravity 62C of the anti-balancer side weight section 612B are shown. The first center of gravity 61G of the balancer side weight section 612A and the second center of gravity 62C of the anti-balancer side weight section 612B are on the Y axis because the weight section 612 is symmetrical to the Y axis and has a smooth semicircular shape. This is because it has Note that the flange portion 611 provided on the balancer portion 61B will be described later.

The planar shape and dimensions of the balancer side weight part 612A and the anti-balancer side weight part 612B are set according to the physique (capacity, dimensions, rotation speed, etc.) of the scroll compressor 100, and they are not necessarily smooth half-shaped. A circular shape is not adopted. Also, what is important for a balancer is the product of the distance from the center of gravity of the balancer from the rotation axis 6CL (corresponding to the distance from the origin C in the X-Y axis coordinates) and the weight of the balancer. The reason is that it is large. If the distance is increased, the weight can be reduced, but the spatial dimension becomes larger.

In the first embodiment, since the relationship is "weight of the balancer side weight part>weight of the anti-balancer side weight part", for example, the weight ratio of the balancer side weight part 612A and the anti-balancer side weight part 612B is, for example, 4. :1. In other words, the area ratio in at least one cross section perpendicular to the rotating shaft 6CL is, for example, 4:1. That is, the area in a cross section perpendicular to the rotation axis 6CL has a relationship of "area of the balancer side weight part 612A>area of the anti-balancer side weight part 612B". Thereby, the relationship of "weight of balancer side weight part 612A>weight of anti-balancer side weight part 612B" can be easily obtained.

Next, in FIG. 4B, the reason for using "max", which is described as radius R1max and radius R2max, for example, will be described. The radius R1max of the balancer side weight portion 612A and the radius R2max of the anti-balancer side weight portion 612B have a smooth arc shape. However, the present invention is not limited to this, and for example, the balancer side weight portion 612A and the anti-balancer side weight portion 612B may have a partially elliptical shape or an arcuate shape having an uneven shape (described later in the figure). 24 to illustrate this example). In that case, the radius R1max refers to a location corresponding to the maximum distance of the balancer side weight portion 612A, and the radius R2max refers to a location equivalent to the maximum distance of the anti-balancer side weight portion 612B.

Therefore, "max" is used in consideration of such an elliptical or uneven arcuate shape. Note that the point that the arc shape of the balancer portion 61B is partially elliptical or partially uneven is the same in the following embodiments, so a description thereof will be omitted as appropriate. Here, the relationship with 1/2 of the diameter d of the main bearing portion 61A, that is, d/2, has a radius R2max≧d/2, but in the first embodiment, the radius R2max of the balancer portion 61B is larger. It is set.

As shown in FIGS. 3 and 4, the balancer portion 61B includes a flange portion 611 having a semicircular planar shape, a semicircular balancer side weight portion 612A having a radius R1max, and a semicircular anti-balancer side weight portion having a radius R2max. It is constituted by a weight part 612 having a shape that connects with a weight part 612B. In the flange portion 611 shown in FIG. 4, a distance 611Rmin from the rotating shaft 6CL to the outermost diameter is set to be larger than d/2 of the main bearing portion 61A. In other words, there is a relationship of distance 611Rmin>d/2. Note that the relationship between the distance 611Rmin and the radius R1max of the balancer side weight portion 612A is set as distance 611Rmin<radius R1max, but is not limited to this.

Note that the flange portion 611 has a function of supporting a bearing provided between the crankshaft 6 and the second frame 5 in the axial direction.

Other examples will be explained using figures. 5A is a side view of another crankshaft according to the first embodiment, and FIG. 5B is a cross-sectional projection view taken along the line AA of the other crankshaft shown in FIG. 5A. In FIG. 5B, the balancer side weight part 612A has a semicircular shape with a vertical straight part LC1 at a predetermined distance L1 from the Y axis in the first quadrant, and the anti-balancer side weight part 612B has a predetermined distance L1 from the Y axis in the fourth quadrant. It has a semicircular shape with a straight line portion LC2 in the Y-axis direction at a distance L2. Note that the term "predetermined" refers to "a value or thing set in advance," and the same applies to the following description, so the description thereof will be omitted as appropriate. Further, the second center of gravity 62C of the anti-balancer side weight portion 612B and the first center of gravity 61G of the balancer side weight portion 612A have an angle θ about the origin C.

The straight line portion LC1 is a side formed parallel to the Y-axis. Note that in this application, the term "side" refers to a "portion formed in a straight line." Since the content is the same in the following embodiments, the description thereof will be omitted as appropriate. The straight line portion LC2 formed in the anti-balancer side weight portion 612B corresponds to one of the first sides formed in either the third quadrant or the fourth quadrant of the XY coordinate, or both, and here, This corresponds to the first side formed in the fourth quadrant. Further, the straight line portion LC2 is formed parallel to the Y axis.

Note that the above-mentioned parallelism includes not only strict parallelism but also parallelism that includes an error range in processing. Moreover, since the parallelism is the same in the following embodiments, the explanation thereof will be omitted as appropriate.

Although FIG. 5B shows that the first quadrant has the straight line part LC1 and the fourth quadrant has the straight line part LC2, it is also possible to form each of them in the balancer part 61B provided in the second and third quadrants. It may also be a combination of these shapes. Furthermore, although the planar shape of the flange 611 is semicircular in consideration of workability, the role of the flange 611 is to support the sleeve bearing 65, so the planar shape is not limited to the semicircular shape.

Next, the positional relationship between the first center of gravity 61G of the balancer side weight section 612A and the second center of gravity 62C of the anti-balancer side weight section 612B will be explained using FIG. 5B. This also applies to the case where the planar shape of the balancer portion 61B is not the smooth semicircular shape as described above, and this will be explained below. In the XY coordinates passing through the first center of gravity 61G of the balancer side weight section 612A and perpendicular to the rotation axis 6CL of the crankshaft 6, a line passing through the first center of gravity 61G of the balancer side weight section 612A and the origin C and the anti-balancer The angle θ formed by a line passing through the second center of gravity 62C of the side weight portion 612B and the origin C is preferably set to 180 degrees, and at least 90 degrees or more and 270 degrees or less. An example of the angle θ is shown in FIG. 5B.

In FIG. 4B, in an XY coordinate passing through the first center of gravity 61G of the balancer side weight part 612A of the balancer part 61B and perpendicular to the rotation axis 6CL of the crankshaft 6, the first center of gravity 61G of the balancer side weight part 612A and the rotation axis The X-Y coordinate is divided into two by the X-axis, which is perpendicular to the line connecting the points passing through 6CL, and the balancer side weight part 612A is on the side where the first center of gravity 61G is located, and the second center of gravity 62C is on the other side. The side becomes the anti-balancer side weight part 612B. In the cross-sectional shape of the balancer part 61B of the crankshaft 6 in the XY coordinates, if the maximum distance from the origin C is the radius R1max of the arc of the balancer side weight part 612A and the radius R2max of the arc of the anti-balancer side weight part 612B. , the former is set to be larger.
Radius R1max>Radius R2max

Note that a balancer 66 is provided on the L side of the crankshaft 6 shown in FIG. 2 in order to offset the imbalance caused by the swinging of the swinging scroll 32. The crankshaft 6 is made of a forged or cast steel product, or an alloy made by sintering metal powder, and is seamlessly and integrally formed from the same forming material. All parts including the balancer portion 61B are finished into a predetermined shape and size by machining, for example, N/C (Numerical Control) machining. Note that the balancer portion 61B may be subjected to additional processing in order to improve the balance of the scroll compressor 100.

In the scroll compressor 100 equipped with the crankshaft 6 configured as described above, the balancer section 61B provided on the crankshaft 6 rotates to offset the centrifugal force of the swinging scroll 32 that swings eccentrically. , prevent bearing seizure and wear. Moreover, since the balancer part 61B is provided as an integral part of the crankshaft 6, a ring part for shrink fitting can be eliminated, so that the weight part 612 can be downsized and the rigidity of the crankshaft 6 can be improved.

Further, with such a configuration, there is no need to attach a balance weight, and therefore, the scroll compressor 100 can be assembled easily and in a short time, and an inexpensive scroll compressor 100 can be provided. In addition, since the rigidity of the crankshaft 6 is improved, the reliability of the scroll compressor 100 is improved, and it becomes possible to increase the amount of refrigerant compression and increase the number of rotations used. Furthermore, as shown in FIG. 2, it is possible to provide a sleeve bearing 65 between the bearing section 22 of the first frame 2 and the main bearing section 61A of the crankshaft 6, further improving reliability.

In addition, by machining all parts of the crankshaft 6, including the balancer part 61B, the weight and center of gravity can be controlled with high precision, and the centrifugal force of the oscillating scroll 32 can be offset with high precision, resulting in less vibration and higher reliability. You can improve.

In addition, since the balancer side weight part 612A and the anti-balancer side weight part 612B are provided connected to the XY coordinate including the rotation axis 6CL of the crankshaft 6, here the Y axis, the balancer side weight part 612A and the anti-balancer side weight part 612A are connected to the If each of the balancer side weight portions 612B is formed symmetrically with respect to the XY coordinates, for example, as shown in FIG. 4, the center of gravity position can be easily controlled. Therefore, since the centrifugal force of the swinging scroll 32 can be offset with high precision, the reliability can be improved with less vibration.

Furthermore, by forming the flange portion 611, the balancer side weight portion 612A, and the anti-balancer side weight portion 612B in a semicircular shape centered on the origin C with respect to the balancer portion 61B, other portions of the crankshaft 6 can be processed simultaneously. Since they can be processed simultaneously, the center of gravity can be easily controlled. Therefore, since the centrifugal force of the swinging scroll 32 can be offset with high precision, the reliability can be improved with less vibration.

Furthermore, since the distance 611Rmin from the rotating shaft 6CL to the outermost diameter is larger than d/2 of the main bearing portion 61A, the diameter of the balancer portion 61B becomes thicker, thereby improving rigidity and reliability.

Furthermore, as shown in FIG. 24, a portion of the outer shape of the anti-balancer side weight portion 612B may be formed into an elliptical shape 612BB. Then, side S22 and side S23 are formed. The side S22 and the side S23 formed on the anti-balancer side weight portion 612B correspond to one of the first sides formed in either the third quadrant or the fourth quadrant of the XY coordinate, or both. S22 corresponds to the first side formed in the fourth quadrant, and side S23 corresponds to the first side formed in the third quadrant. Further, the side S22 and the side S23 are formed parallel to the Y axis. In this way, by forming the elliptical shape 612BB or alternatively an uneven shape (a shape having an uneven surface), the total weight of the balancer section 61B can be reduced, and the weight section 612 can be made smaller.

Further, the angle θ formed by the line passing through the first center of gravity 61G of the balancer side weight portion 612A and the origin C and the line passing through the second center of gravity 62C of the anti-balancer side weight portion 612B and the origin C is preferably 180 degrees, By setting the angle to at least 90 degrees or more and 270 degrees or less, the weight of the anti-balancer side weight section 612B can be reduced, and the weight section 612 can be made smaller. Furthermore, since the centrifugal force of the swinging scroll 32 can be offset with high precision, there is less vibration and reliability can be improved.

In the above description, for the sake of simplicity, the second center of gravity of the anti-balancer side weight part 612B must be located on the XY coordinate passing through the first center of gravity 61G of the balancer side weight part 612A and perpendicular to the rotation axis 6CL of the crankshaft 6. 62C exists, but the present invention is not limited to this. If the second center of gravity 62C of the anti-balancer side weight portion 612B does not exist on the XY coordinates, the second center of gravity 62C of the anti-balancer side weight portion 612B exists on the XY coordinates along the rotation axis 6CL direction. The point transferred can be considered as a substitute for the second center of gravity 62C. Note that this matter is the same in the following embodiments, so the explanation thereof will be omitted as appropriate.

According to the scroll compressor of Embodiment 1 configured as described above,
A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, Since the main shaft part of the crankshaft is provided with a balancer part formed as an integral part that reduces the unbalanced force accompanying the rotation of the crankshaft,
Since the unbalanced force accompanying the rotation of the crankshaft can be reduced in the balancer section, assembly work is easy and compactness is possible.

Furthermore, according to the scroll compressor of Embodiment 1,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Since the weight of the balancer side weight part>the weight of the anti-balancer side weight part holds,
The area of at least one cross section perpendicular to the rotation axis is
Since the area of the balancer side weight part>the area of the anti-balancer side weight part is satisfied,
By simply setting the relationship: area of balancer side weight portion>area of the anti-balancer side weight portion, a balancer portion that can reduce the unbalanced force accompanying rotation of the crankshaft can be easily obtained.

Furthermore, according to the scroll compressor of Embodiment 1,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
Since the anti-balancer side weight part has a first side in either the third quadrant or the fourth quadrant of the coordinates, or both,
By forming the first side,
The relationship of area of balancer side weight portion>area of the anti-balancer side weight portion can be easily obtained.

Furthermore, according to the scroll compressor of Embodiment 1,
Since the first side is formed by a side parallel to the Y axis,
It can be processed using a general-purpose machine such as a 2-axis lathe. Additionally, since other parts can be processed at the same time, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll can be offset with high precision, resulting in less vibration and improved reliability. Additionally, since it can be processed using general-purpose machinery, equipment investment is reduced and costs can be reduced.

Furthermore, according to the scroll compressor of Embodiment 1,
The balancer side weight part has a side parallel to the Y-axis and having a distance L1 from the Y-axis in either the first quadrant or the second quadrant of the coordinates,
The first side of the anti-balancer side weight part has a first side parallel to the Y-axis and having a distance L2 from the Y-axis,
Since the relationship of distance L1>distance L2 and the parallel side and the parallel first side are formed on the same side with respect to the Y axis,
The relationship of area of the balancer side weight portion>area of the anti-balancer side weight portion can be easily and reliably obtained.
Furthermore, it can be processed using a general-purpose machine such as a two-axis lathe. Additionally, since other parts can be processed at the same time, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll can be offset with high precision, resulting in less vibration and improved reliability. Additionally, since it can be processed using general-purpose machinery, equipment investment is reduced and costs can be reduced.

Furthermore, according to the scroll compressor of Embodiment 1,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
The balancer side weight part and the anti-balancer side weight part have a semicircular shape centered on the origin, and the maximum distance of the semicircle from the origin is:
Since the maximum distance of the balancer side weight part>the maximum distance of the anti-balancer side weight part is formed,
The relationship of area of the balancer side weight portion>area of the anti-balancer side weight portion can be easily and reliably obtained.

Furthermore, according to the scroll compressor of Embodiment 1,
Since a part of the outer shape of the anti-balancer side weight part is formed in an elliptical shape or an uneven shape,
The total weight of the balancer section can be reduced, making it possible to downsize.

Furthermore, according to the scroll compressor of Embodiment 1,
Centered on the origin,
Since the angle between a line passing through the first center of gravity of the balancer side weight part and the origin and a line passing through the second center of gravity of the anti-balancer side weight part and the origin is 90 degrees or more and 270 degrees or less,
The weight of the anti-balancer side weight part can be reduced and the size can be reduced. Furthermore, since the centrifugal force of the oscillating scroll can be offset with high precision, there is less vibration and reliability can be improved.

Furthermore, according to the scroll compressor of Embodiment 1,
Since the balancer section is provided with a collar section that is connected to the balancer side weight section in the axial direction,
The balancer part can be easily supported at other locations by the collar part.

Furthermore, according to the scroll compressor of Embodiment 1,
Since the entire shape of the crankshaft is formed by machining,
The center of gravity can be easily controlled and the centrifugal force of the oscillating scroll can be offset with high precision, resulting in less vibration and improved reliability.

Note that in the following embodiments as well, similar to the first embodiment,
The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
In the X-Y coordinates,
Since they are similar in that they have the relationship: area of balancer side weight section>area of anti-balancer side weight section, the explanation thereof will be omitted as appropriate.

Embodiment 2.
Next, the crankshaft 6 of Embodiment 2 will be explained based on the drawings. 6A is a side view of the crankshaft according to the second embodiment, and FIG. 6B is a top view of the crankshaft according to the second embodiment as seen from the U side (arrow Z) direction in FIG. 6A. Note that FIG. 7A shows an enlarged view of the balancer portion 61B in FIG. 6A, and FIG. 7B shows a cross-sectional projection view taken along the line AA in FIG. 6A. In the figures, the same parts as in the first embodiment are given the same reference numerals, and the explanation will be omitted.

As shown in each figure, the balancer portion 61B has a configuration in which the flange portion 611 shown in FIGS. 3A and 3B of the first embodiment described above is not provided. That is, the balancer section 61B is provided with a balancer side weight section 612A and an anti-balancer side weight section 612B. Other than this, the second embodiment is the same as the first embodiment. With this configuration, in addition to the effects of the first embodiment, it is possible to further reduce the size and weight. In the case of this second embodiment, since the structure is not capable of supporting the sleeve bearing 65, as an alternative, the bearing portion 2A of the first frame 2 may be machined or the bearing may be installed by press fitting, etc. to the main bearing portion 61A. Use a compatible bearing.

Further, in the case of the shape shown in FIG. 7B, the shape can be formed by forging or casting, so it can be formed without the need for cutting. The same applies to the case shown in FIG. 4B of the first embodiment. Further, in the case of FIG. 5B of the first embodiment, the straight portion LC1 and the straight portion LC2 can be formed by cutting from the state shown in FIG. 4B.

According to the scroll compressor of the second embodiment configured as described above, the same effects as those of the above embodiment are achieved, and
Since no flange is provided, it is possible to reduce the size and weight.

Embodiment 3.
Next, the crankshaft 6 of Embodiment 3 will be explained based on the drawings. 8A is a side view of the crankshaft according to the third embodiment, and FIG. 8B is a top view of the crankshaft according to the third embodiment as seen from the U side (arrow Z) direction of FIG. 8A. Note that FIG. 9A shows an enlarged view of the balancer portion 61B in FIG. 8A, and FIG. 9B shows a cross-sectional projection view taken along the line AA in FIG. 9A. Further, in FIG. 16, the first side formed in either the third quadrant or the fourth quadrant of the XY coordinates, or both will be explained. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted.

As shown in FIG. 9, the planar shape of the anti-balancer side weight portion 612B is a rectangular shape formed by a straight portion 612S. The rectangular shape of the anti-balancer side weight portion 612B is such that the straight portions 612S having a width W1 are connected at a distance H3 from the X axis. The intersection of the distance H3 and the width W1 intersects with the circumference of the radius R2max, but is not limited thereto. The straight portion 612S forming the lower surface of the rectangular shape is parallel to the X axis. Further, the balancer side weight portion 612A has the same shape as that shown in FIG. 4 in the first embodiment. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has the same effects as the first embodiment.

Next, the first side and the second side formed on the anti-balancer side weight portion 612B in the third embodiment will be described using FIG. 16.
First, the first side refers to a side (straight line part) formed in either or both of the third quadrant and fourth quadrant of the coordinates in the anti-balancer side weight section. Further, the second side is a coordinate in a plane perpendicular to the rotational axis of the crankshaft, and refers to a side (straight line part) that is continuous to the first side of the balancer portion 61B. Note that the relationship between the first side and the second side is the same in the following embodiments, so the description thereof will be omitted as appropriate.

As shown in FIG. 16, the straight portions 612S of the anti-balancer side weight portion 612B are defined as sides S11, S12, and S13, respectively. Therefore, any one of the sides S11, S12, and S13 corresponds to the first side formed in the third quadrant, the fourth quadrant, or both of the coordinates in the anti-balancer side weight portion 612B. If the side S11 is the first side, the side S12 corresponds to the side continuous to the side S11, that is, the second side.

Further, if the side S12 is the first side, both the side S12 and the side S13 correspond to sides that are continuous to the side S12, that is, the second side. The side S11 is formed in the fourth quadrant of the XY coordinates and parallel to the Y axis. The side S12 is formed to be connected to both the third and fourth quadrants of the XY coordinates, and is formed parallel to the X axis. The side S13 is formed in the third quadrant of the XY coordinates and parallel to the Y axis.

In this manner, by providing the side S12 parallel to the X axis, other parts of the crankshaft 6 can be machined simultaneously with a general-purpose machine such as a two-axis lathe. In addition, since they can be processed simultaneously, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll 32 can be offset with high precision, so that vibrations are reduced and reliability can be improved. Additionally, since it can be processed using general-purpose machinery, equipment investment is reduced and production can be made at low cost.

Further, the anti-balancer side weight portion 612B is formed in a shape having sides S11 and S13 having a distance H3 from the X axis in the XY coordinate. Therefore, the weight of the anti-balancer side weight part 612B can be reduced without significantly impairing the rigidity of the crankshaft 6, and the weight part 612 can be made smaller, and a larger centrifugal force can be canceled. . Moreover, since it is a straight line, it can be easily machined with a cutting tool such as an end mill.

Further, 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 the second embodiment.

According to the scroll compressor of Embodiment 3 configured as described above, the same effects as those of the above embodiments are achieved, and
Coordinates in a plane perpendicular to the rotation axis of the crankshaft,
Since the balancer section has a second side that is continuous with the first side,
The relationship of area of the balancer side weight portion>area of the anti-balancer side weight portion can be easily and reliably obtained.

Furthermore, according to the scroll compressor of Embodiment 3,
The balancer side weight part has a semicircular shape centered on the origin,
Since the anti-balancer side weight portion is formed in a polygonal shape,
The relationship of area of the balancer side weight portion>area of the anti-balancer side weight portion can be easily and reliably obtained.

Furthermore, according to the scroll compressor of Embodiment 3,
The maximum distance of the semicircular shape of the balancer side weight part is R1max,
If the maximum distance of the anti-balancer side weight portion in the X-axis direction is W1,
Since it was formed with the relationship R1max>W1,
The relationship of the area of the balancer side weight portion>the area of the anti-balancer side weight portion can be obtained more easily and reliably.

Embodiment 4.
Next, the crankshaft 6 of Embodiment 4 will be explained based on the drawings. 10A is a side view of the crankshaft according to the fourth embodiment, and FIG. 10B is a top view of the crankshaft according to the fourth embodiment as seen from the U side (arrow Z) direction in FIG. 10A. Note that FIG. 11A shows an enlarged view of the balancer portion 61B in FIG. 10A, and FIG. 11B shows a cross-sectional projection view taken along the line AA in FIG. 11A. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted.

As shown in FIG. 11, the balancer side weight part 612A and the anti-balancer side weight part 612B have a substantially inversely convex shape as a whole. The balancer side weight portion 612A has a circular arc with a radius R1max, and has a substantially mushroom-shaped shape with a width W1 parallel to the X-axis until it reaches a position a predetermined distance H1 from the X-axis, and the anti-balancer side weight The portion 612B extends W1 to a position at a distance H2 from the X-axis, and includes a diagonal line connecting a straight line parallel to the X-axis having a width W2 at a position a predetermined distance H3 from the X-axis and W1 at a position at the distance H2. It has a shape that connects.

Of the substantially mushroom shape, a straight portion 612S is provided on the side opposite to the balancer side weight portion 612B. Referring to FIG. 17, which will be described later, the intersection of sides S18 and S17, the intersection of sides S17 and S16, the intersection of sides S16 and S15, and the intersection of sides S15 and S14 are shown in FIG. 11B. Although it intersects with the circumference of radius R2max, it is not limited to this. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has the same effects as the first embodiment.

Next, the first side and the second side in the fourth embodiment will be explained using FIG. 17. In the figure, each side is defined as side S14, side S15, side S16, side S17, side S18, side V11, and side V14. Therefore, any one of side S14, side S15, side S16, side S17, and side S18 is the first side formed in either the third quadrant, the fourth quadrant, or both of the coordinates in the anti-balancer side weight portion 612B. Corresponds to the edge. Further, the side V11 and the side V14 correspond to a second side continuous to the first side.

If the side S16 is the first side, the side S15 and the side S17 correspond to the sides continuous with the side S16, that is, the second side. Further, if side S14 is the first side, side S15 and side V11 correspond to sides continuous with side S14, that is, the second side. Further, if side S18 is the first side, side S17 and side V14 correspond to sides continuous with side S18, that is, the second side. Further, if side S15 is the first side, side S14 and side S16 correspond to sides continuous with side S15, that is, the second side. Further, if side S17 is the first side, side S18 and side S16 correspond to sides continuous with side S17, that is, the second side.

The side S14 is formed to be connected to both the first quadrant and the fourth quadrant of the XY coordinate, and is formed parallel to the Y axis. The side S15 is formed in the fourth quadrant of the XY coordinates.

The side S16 is formed to be connected to both the third and fourth quadrants of the XY coordinates, and is formed parallel to the X axis. The side S17 is formed in the third quadrant of the XY coordinates. The side S18 is formed to be connected to both the second quadrant and the third quadrant of the XY coordinate, and is formed parallel to the Y axis. Side V11 is formed in the first quadrant of the XY coordinates and intersects side S14 at a right angle. However, it is not limited to a right angle. Side V14 is formed in the second quadrant of the XY coordinates and intersects side S18 at a right angle. However, it is not limited to a right angle.

In addition, the anti-balancer side weight portion 612B has a width W1 extending from the X-axis to a position at a distance H2, and a straight line parallel to the X-axis having a width W2 at a position at a predetermined distance H3 from the X-axis and a position at a distance H2. By having a shape connected to the width W1 by a diagonal line, the weight of the anti-balancer side weight portion 612B can be reduced, and the weight portion 612 can be made smaller. Also, larger cancellations are possible.

In addition, the anti-balancer side weight portion 612B has (a part of) a side S14 and (a part of) a side S18 which are straight portions 612S having a length of a distance H2 from the X axis in the XY coordinate, and a width W1. It is formed to include (part of) side S14 and (part of) side S18, which are straight line portions 612S. Therefore, the weight of the anti-balancer side weight section 612B can be further reduced without significantly reducing the rigidity of the crankshaft 6, and the weight section 612 can be further downsized, and a larger centrifugal force can be canceled. play. Moreover, since it is a straight line, it can be easily processed with a cutting tool such as an end mill.

Further, the anti-balancer side weight portion 612B is connected to (part of) side S14 and (part of) side S18 having distance H2 in the XY coordinate, and side S15 or side S17 and It is formed with a side S16 parallel to the axis. Therefore, the weight of the anti-balancer side weight section 612B can be further reduced without significantly reducing the rigidity of the crankshaft 6, and the weight section 612 can be further downsized, and a larger centrifugal force can be canceled. play.

In addition, in the case of the shape shown in FIG. 17, from the state shown in FIG. 7B of the second embodiment, since the sides S14 to S18 are straight lines, it can be easily machined with a cutting tool such as an end mill. play. Further, it is preferable that the distance H1 and the distance H2 be the same length. By setting distance H1=distance H2, other parts of the crankshaft 6 can be machined simultaneously with a general-purpose machine such as a two-axis lathe. Since they can be processed simultaneously, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll 32 can be offset with high precision, so that vibrations are reduced and reliability can be improved. In addition, since it can be processed using general-purpose machinery, investment is reduced and manufacturing is possible at low cost.

Here, the first side, the second side, and other examples will be described based on FIGS. 18, 25, and 26. Note that FIGS. 18 and 26 only show the planar shape of the balancer portion 61B in the XY coordinates as in each of the above embodiments, and other parts are omitted. Further, FIG. 25 is a cross-sectional view showing the configuration of the member before forming the balancer portion 61B in the XY coordinate, as in each of the above embodiments, and only the planar shape is shown.

First, when obtaining the balancer part 61B as shown in FIGS. 18 and 26, in the present application, for example, the balancer part 61B of the present application is cut from a cylindrical member formed by cylindrical forging or casting. Manufacture. Therefore, before cutting, as shown in FIG. 25, it has a circular shape 600 in the XY coordinates. A case will be described in which cutting is performed from the circular shape 600 to form the balancer portion 61B.

In FIG. 18A, a side S19 as a first side connected to the third and fourth quadrants is formed in the anti-balancer side weight portion 612B. This is an example in which the second side that is continuous with the first side is not formed. FIG. 18B is an example in which the first side and the second side are not formed. The balancer side weight portion 612A has a side V15 formed in the first quadrant and a side V16 formed in the second quadrant.

In FIG. 18C, a side S20 as a first side is formed in the fourth quadrant of the anti-balancer side weight portion 612B. Then, a side connected to the side S20 is formed as a side V17 in the first quadrant of the balancer side weight portion 612A. Therefore, side V17 corresponds to the second side. In FIG. 18D, a side S21 as a first side is formed continuously from the fourth quadrant of the anti-balancer side weight part 612B to the balancer side weight part 612A.

In FIG. 26A, a side S24 is formed as a first side connected to the third and fourth quadrants of the anti-balancer side weight portion 612B. This is an example in which the second side that is continuous with the first side is not formed. In FIG. 26B, a side S25 as the first side is formed in the third quadrant of the anti-balancer side weight portion 612B, and a side S26 as the first side is formed in the fourth quadrant. This is an example in which the second side that is continuous with the first side is not formed.

In FIG. 26C, a side S27 is formed in the third quadrant and a side S27 is formed in the fourth quadrant of the anti-balancer side weight portion 612B. Therefore, either side S26 or side S25 corresponds to the first side formed in either the third quadrant or the fourth quadrant of the coordinates, or both, in the anti-balancer side weight portion 612B. If the side S27 is the first side, the side S28 corresponds to the side continuous to the side S27, that is, the second side. Furthermore, if the side S28 is the first side, the side S27 corresponds to the side continuous to the side S28, that is, the second side.

In FIG. 26D, a side S29, a side S30, and a side S31 are formed on the anti-balancer side weight portion 612B. Therefore, any one of side S29, side S30, and side S31 corresponds to the first side formed in either the third quadrant, the fourth quadrant, or both of the coordinates in the anti-balancer side weight portion 612B. If the side S29 is the first side, the side S30 corresponds to the side continuous to the side S29, that is, the second side.

Furthermore, if the side S30 is the first side, both the side S29 and the side S31 correspond to sides that are continuous to the side S30, that is, the second side. Further, if side S31 is the first side, side S30 corresponds to a side continuous to side S31, that is, a second side. The side S31 is formed in the fourth quadrant of the XY coordinates. The side S30 is formed to be connected to both the third and fourth quadrants of the XY coordinates, and is formed parallel to the X axis. The side S29 is formed in the third quadrant of the XY coordinates.

As shown above, in the balancer section 61B, the area of the balancer side weight section 612A and the anti-balancer side weight section 612B in the XY coordinates is
If the relationship is such that the area of the balancer side weight part 612A>the area of the anti-balancer side weight part 612B, then the first side formed on the anti-balancer side weight part 612B and the side continuous to the first side, that is, the second side. Various examples can be considered regarding the formation of edges.

Further, the anti-balancer side weight portion 612B is formed in a polygonal shape including a first side and a second side, and by making the sides perpendicular or parallel, the first side and the second side are simultaneously Since it can be manufactured using tools, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll can be offset with high precision, resulting in less vibration and improved reliability.

Furthermore, it can be processed using a general-purpose machine such as a two-axis lathe. Additionally, since other parts can be processed at the same time, the center of gravity can be easily controlled. Therefore, the centrifugal force of the oscillating scroll can be offset with high precision, resulting in less vibration and improved reliability. Additionally, since it can be processed using general-purpose machinery, equipment investment is reduced and costs can be reduced.

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 part is formed in a mushroom shape having a semicircular shape centered on the origin and a polygonal shape connected to the semicircular shape,
Since the anti-balancer side weight portion is formed in an inverse convex shape that is continuous with the polygonal shape,
The relationship of area of the balancer side weight portion>area of the anti-balancer side weight portion can be easily and reliably obtained.

Furthermore, according to the scroll compressor of Embodiment 4,
If the maximum distance of the semicircular shape of the balancer side weight part is R1max, and the maximum distance of the anti-balancer side weight part in the X-axis direction is W1,
Since it was formed with the relationship R1max>W1,
The relationship of the area of the balancer side weight portion>the area of the anti-balancer side weight portion can be obtained more easily and reliably.

Embodiment 5.
Next, the crankshaft 6 of Embodiment 5 will be explained based on the drawings. 12A is a side view of the crankshaft according to the fifth embodiment, and FIG. 12B is a top view of the crankshaft according to the fifth embodiment as seen from the U side (arrow Z) direction in FIG. 12A. Note that FIG. 13A shows an enlarged view of the balancer portion 61B in FIG. 12A, and FIG. 13B shows a cross-sectional projection view taken along the line AA in FIG. 12A. 14A is a side view of another crankshaft according to Embodiment 5, and FIG. 14B is a sectional projection view taken along the line AA of the crankshaft shown in FIG. 14A. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted.

As shown in FIG. 13, the balancer side weight portion 612A is the same as that in FIG. 4 of the first embodiment described above. The anti-balancer side weight portion 612B has a planar shape similar to that in FIG. 9B of the third embodiment described above, and extends from a position a predetermined distance H4 away from the X-axis to a distance H3, and has a width in the axial direction from the end surface of the main bearing portion 61A. A notch 612K as a recess is provided at a position WL2 across the width WL1 in the direction of the rotating shaft 6CL. The distance H4 has the same dimension as d/4, but is not limited to this.

As shown in FIGS. 14A and 14B, instead of the cut portion 612K, a drill hole 612R may be provided as a recess having a predetermined diameter DR in the anti-balancer side weight portion 612B. The depth of the drill hole 612R is set to d/4, but is not limited to this. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has the same effects as the first embodiment. Although the fifth embodiment uses a drilled hole 612R, the shape of the hole and the method of machining are not limited, such as a blind hole formed by an end mill.

According to the scroll compressor of Embodiment 5 configured as described above, the same effects as those of the above embodiments are achieved, and
Since the anti-balancer side weight portion is formed with a recess,
The weight part can be made lighter.

Moreover, according to the scroll compressor of Embodiment 5,
Further, the anti-balancer 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. Therefore, the recess can be easily obtained using the notch.

Moreover, according to the scroll compressor of Embodiment 5,
Further, since a hole having a predetermined diameter is provided on the Y axis of the polygonal portion of the weight portion on the opposite balancer side, the recess can be easily formed by the hole.

Embodiment 6.
Next, Embodiment 6 will be described. The purpose of this sixth embodiment is to improve the flow of refrigerant within the middle shell 11 shown in FIG. 2 in order to further improve the efficiency of the scroll compressor 100. The tooth tip of the first spiral body 312 of the fixed scroll 31 of the compression drive unit 3 shown in FIG. Assuming that the gap between them is Q, a method for adjusting this gap Q will be explained using FIG. Note that FIG. 15 is a partially enlarged sectional view of the compression drive section 3 of FIG. 2. As shown in FIG. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted.

When the dimensions of each part are set as follows, the gap Q between the tip of the first spiral body 312 of the fixed scroll 31 and the surface UA on the one end side of the second substrate 321 of the oscillating scroll 32 is as follows. It can be expressed by the formula.

L=M+Q+N+T+P
Therefore,
Q=L-M-N-T-P
Here,
L: Distance between the first positioning surface 113 of the middle shell 11 and the second positioning surface 116 of the middle shell 11 M: The tip of the teeth of the first positioning surface 113 of the middle shell 11 and the first spiral body 312 of the fixed scroll 31 N: Thickness of the second substrate 321 of the orbiting scroll 32 T: Thickness of the thrust plate 24 P: Distance between the second positioning surface 116 of the middle shell 11 and the flat surface 212 of the first frame 2

Here, if the dimensions of each part are known by measurement, a desired gap Q can be set by adjusting the thickness T of the thrust plate 24, which enables production of a wide variety of products in large quantities. By adjusting this gap Q, it is possible to prevent the refrigerant from leaking into the compression space through the gap Q, so it is possible to reduce the loss of the scroll compressor 100.

According to the scroll compressor of Embodiment 6 configured as described above, the same effects as those of the above-mentioned embodiments are achieved, and
Since the thrust plate is provided between the first frame of the compression drive unit and the second substrate of the oscillating scroll,
Leakage of refrigerant introduced into the scroll compressor can be suppressed.

Embodiment 7.
Next, Embodiment 7 will be described. 19A is a side view of the crankshaft according to the seventh embodiment, and FIG. 19B is a cross-sectional projection view taken along line AA of the crankshaft shown in FIG. 19A. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted. As shown in FIG. 19, a mark section 201 such as a QR code (registered trademark) as an individual discrimination section for identifying an individual may be provided on the linear section 612S of the anti-balancer side weight section 612B.

When a crankshaft has no or almost no flat surface and the curvature of the curved surface is small, it is difficult to provide an individual discrimination section for individual discrimination. However, in the present application, since the anti-balancer side weight part 612B has the straight part 612S, it is possible to manage the individual by providing a mark part 201 such as a QR code (registered trademark) for identifying the individual, and the defect rate is It is possible to improve the functionality of the compressor, such as reducing the amount of noise and selecting combinations.

In this embodiment, the mark portion 201 is provided on the linear portion 612S of the anti-balancer side weight portion 612B, but it may be provided on the outer circumference side of the radius R1max of the balancer side weight portion 612A. By forming the balancer side weight part 612A and the crankshaft 6 seamlessly and integrally with the same material, the balancer side weight part 612A has a larger radius than a general crankshaft, so the curvature is small, and the The individual discrimination section can be provided more easily than in the conventional case, and by providing the individual discrimination section, individual control can be performed, and the scroll compressor 100 can be highly functional, such as reducing the defective rate and selecting combinations.

According to the scroll compressor of Embodiment 7 configured as above, the same effects as those of the above embodiments are achieved, and
Since the balancer section is provided with an individual discrimination section,
Individual management is possible, reducing the defective rate and improving the functionality of scroll compressors such as combination selection.

Embodiment 8.
Next, Embodiment 8 will be described. 20A is a side view of the crankshaft according to the eighth embodiment, and FIG. 20B is a top view of the crankshaft according to the eighth embodiment. FIG. 21 is a sectional view of a scroll compressor according to Embodiment 8. FIG. 22 is a partial sectional view of a scroll compressor according to Embodiment 8. FIG. 23 is a partial sectional view of another scroll compressor according to Embodiment 8. In the figures, parts similar to those in each of the above embodiments are designated by the same reference numerals, and explanations thereof will be omitted.

As shown in FIGS. 20 to 22, the balancer cover 301 is provided with holes 302 and bolts 303 for fixing bolts etc. on the U side end surface of the balancer portion 61B of the crankshaft 6, not on the first frame 2. Fixed. The balancer cover 301 is attached to a fixing hole 302 provided not on the first frame 2 but on the U-side end surface of the balancer portion 61B of the crankshaft 6 via bolts 303.

Since the balancer cover 301 is integrated with the crankshaft 6 instead of the first frame 2, there is no fear that the balancer portion 61B will deform due to rotation and come into contact with the balancer cover 301. Therefore, the diameter of the balancer portion 61B can be increased. Therefore, it is possible to cope with a larger centrifugal force of the swinging scroll 32, increase the number of rotations of the scroll compressor 100, or enlarge the scroll, and increase the amount of compression of the scroll compressor 100.

Further, the hole 302 is preferably formed near the outer periphery of the balancer weight portion 612A, as shown in FIG. 20B. By providing it on the balancer side weight portion 612A side, the weight of the bolt 303 and the centrifugal force of the swinging scroll can be canceled.

As another example, as shown in FIG. 23, in order to fix the balancer cover 301 to the balancer part 61B, holes 302 and bolts 303 for fixing bolts etc. are inserted around the outer circumference of the balancer side weight part 612A with a radius R1max. It may be provided in the section. Since the bolt 303 is located further away from the rotating shaft 6CL, the centrifugal force of the swinging scroll can be further canceled. Further, when fastening the bolt 303 to the hole 302, a weight 304 may be installed. Note that when fastening the bolts 303, it is preferable to use an adhesive to prevent loosening.

According to the scroll compressor of Embodiment 8 configured as described above, the same effects as in each of the above embodiments are achieved, and
Since the balancer cover is fixedly installed on the balancer section, the balancer cover is integrated with the balancer section, so there is no concern that the balancer section will deform due to rotation and come into contact with the balancer cover.

Although this application describes various exemplary embodiments and examples, the various features, aspects, and functions described in one or more embodiments may be applicable to a particular embodiment. The present invention is not limited to, and can be applied to the embodiments alone or in various combinations.
Therefore, countless variations not illustrated are envisioned within the scope of the technology disclosed herein. For example, this includes cases where at least one component is modified, added, or omitted, and cases where at least one component is extracted and combined with components of other embodiments.

1 shell, 100 scroll compressor, 11 middle shell, 113 first positioning surface, 116 second positioning surface, 12 upper shell, 13 lower shell, 15 discharge pipe, 2 first frame, 212 flat surface, 22 bearing section, 24 thrust plate, 2A bearing section, 3 compression drive section, 301 balancer cover, 302 hole, 303 bolt, 304 weight, 31 fixed scroll, 312 first spiral body, 32 oscillating scroll, 321 second substrate, 322 second spiral body, 34 Compression chamber, 4 Drive section, 4A Rotor, 5 Second frame, 5A Sub-bearing section, 6 Crankshaft, 60 Oil passage, 61 Main shaft section, 611 Flange section, 612 Weight section, 612A Balancer side weight section, 612B Reverse Balancer side weight part, 612BB elliptical shape, 612K notch part, 612R drill hole, 612S straight part, 61A main bearing part, 61B balancer part, 61C rotor shrink-fit part, 61D sub-bearing part, 61G first center of gravity, 62 eccentric shaft part , 62C second center of gravity, 62CL eccentric shaft, 65 sleeve bearing, 66 balancer, 6CL rotating shaft, Q clearance.

Claims (13)

A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Since the weight of the balancer side weight part>the weight of the anti-balancer side weight part holds,
The area of at least one cross section perpendicular to the rotation axis is
having a relationship of area of the balancer side weight part>area of the anti-balancer side weight part,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
In the scroll compressor , the anti-balancer side weight portion is formed from the first side toward the origin . A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have the relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
Coordinates in a plane perpendicular to the rotation axis of the crankshaft,
The balancer section is a scroll compressor having a second side that is continuous with the first side. A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have the relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
The balancer side weight part and the anti-balancer side weight part have a semicircular shape centered on the origin, and the maximum distance of the semicircle from the origin is:
The scroll compressor is formed such that the maximum distance of the weight portion on the balancer side>the maximum distance of the weight portion on the anti-balancer side. The scroll compressor according to any one of claims 1 to 3 , wherein a part of the outer shape of the anti-balancer side weight part is formed in an elliptical shape or an uneven shape. Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
Centered on the origin,
A claim in which the angle between a line passing through the first center of gravity of the balancer side weight part and the origin and a line passing through the second center of gravity of the anti-balancer side weight part and the origin is 90 degrees or more and 270 degrees or less. The scroll compressor according to any one of claims 1 to 4. A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have the relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
The balancer side weight part has a semicircular shape centered on the origin,
In the scroll compressor, the anti-balancer side weight portion is formed in a polygonal shape. A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Weight of the weight part on the balancer side>weight of the weight part on the anti-balancer side
In order to have a relationship of
The area of at least one cross section perpendicular to the rotation axis is
Area of the weight part on the balancer side>Area of the weight part on the anti-balancer side
have the relationship of
Coordinates in a plane perpendicular to the rotational axis of the crankshaft, where a line on a horizontal plane including the rotational axis is the X-axis, a vertical center line of the crankshaft perpendicular to the X-axis is the Y-axis, and the X-axis If we define the point on the rotation axis where and the Y axis intersect as the origin,
A portion of the outer shape of the anti-balancer side weight portion has a first side in either or both of the third quadrant and the fourth quadrant of the coordinates,
The balancer side weight part is formed in a mushroom shape having a semicircular shape centered on the origin and a polygonal shape connected to the semicircular shape,
In the scroll compressor, the anti-balancer side weight portion is formed in an inversely convex shape continuous to the polygonal shape. The maximum distance of the semicircular shape of the balancer side weight part is R1max,
If the maximum distance of the anti-balancer side weight portion in the X-axis direction is W1,
The scroll compressor according to claim 6 or 7, wherein the scroll compressor is formed with a relationship of R1max>W1. The scroll compressor according to any one of claims 1 to 8, wherein the anti-balancer side weight portion has a recess formed therein. A crankshaft supported by a bearing fixed to a shell, a drive section for the crankshaft, an oscillating scroll provided on an eccentric shaft portion of the crankshaft, and a fixed scroll provided on the shell, The main shaft portion of the crankshaft is provided with a balancer portion formed as an integral part that reduces unbalanced force accompanying rotation of the crankshaft,
The balancer section is composed of a balancer side weight section and an anti-balancer side weight section, and the balancer side weight section and the anti-balancer side weight section are connected to a plane including the rotation axis of the crankshaft, and
Since the weight of the balancer side weight part>the weight of the anti-balancer side weight part holds,
The area of at least one cross section perpendicular to the rotation axis is
having a relationship of area of the balancer side weight part>area of the anti-balancer side weight part,
A scroll compressor, wherein the balancer section is provided with a flange section that is connected to the balancer side weight section in the axial direction. The scroll compressor according to any one of claims 1 to 10, wherein a thrust plate is provided between the first frame of the compression drive section and the second substrate of the oscillating scroll. The scroll compressor according to any one of claims 1 to 11, wherein the balancer section is provided with an individual discrimination section. The scroll compressor according to any one of claims 1 to 12, wherein a balancer cover is fixedly installed on the balancer section.

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