Scroll compressor

Abstract

A scroll compressor includes: a crankshaft (6) supported by a bearing fixed to a shell (1); a driving mechanism portion (4) for the crankshaft (6); an orbiting scroll (32) provided in an eccentric sha

Description

TITLE OF THE INVENTION: SCROLL COMPRESSOR TECHNICAL FIELD

[0001] The present disclosure relates to a scroll compressor . BACKGROUND ART

[0002] In some cases, the crankshaft of a scroll compressor has attached thereto a balance weight in order to balance the centrifugal force and the moment that occur around the shaft. As an example, a technology for suppressing deflection of a rotation shaft with use of a balance weight in the following configuration has been disclosed (see Patent Document 1, for example). That is, the configuration includes: a rotation shaft; and a balance weight which has an outer circumferential surface in an annular shape and which is fixed to the rotation shaft and rotates together with the rotation shaft, wherein a recessed portion for adjusting the angular position of the balance weight with respect to the rotation shaft is formed in a part of the outer circumferential surface. PATENT DOCUMENT

[0003] Patent Document 1: Japanese Laid-Open Patent Publication No. 2016-50551 SUMMARY OF THE INVENTION PROBLEMS TO BE SOLVED BY THE INVENTION

[0004] However, in the technology shown in Patent Document 1 above, a balance weight corresponding to the rotation shaft is selected, and the balance weight is attached to the rotation shaft through adjustment of the angle of the balance weight. Therefore, the above technology has problems that: there is a risk of attaching a wrong balance weight; angular misalignment may occur when attaching the balance weight, and thus, for prevention of this, an advanced assembling device, a jig, and complicated assembling work are required; since shrink fit is used to fit the balance weight to the rotation shaft, advanced processing is required; and it is necessary to provide a ring portion for shrink fit, resulting in, for example, increase in size of the balance weight.

[0005] The present disclosure provides a technology for solving the above problems. An object of the present disclosure is to provide a scroll compressor of which assembling work is easy and that is small in size.

[0006] A scroll compressor according to the present disclosure includes: a crankshaft supported by a bearing fixed to a shell; a drive portion for the crankshaft; an orbiting scroll provided to an eccentric shaft portion of the crankshaft; and a fixed scroll provided to the shell. A main shaft portion of the crankshaft is provided with a balancer portion that is formed as an integrally-formed object and that decreases a non-equilibrium force associated with rotation of the crankshaft. EFFECT OF THE INVENTION

[0007] Since the scroll compressor according to the present disclosure adopts the configuration as described above, the present disclosure has an effect that a scroll compressor of which assembling work is easy and that is small in size is provided. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] [FIG. 1] FIG. 1 is a perspective view of a scroll compressor according to embodiment 1. [FIG. 2] FIG. 2 is a sectional view of the scroll compressor according to embodiment 1. [FIG. 3] FIG. 3A is a side view of a crankshaft according to embodiment 1, and FIG. 3B is a top view of the crankshaft according to embodiment 1. [FIG. 4] FIG. 4A is a side view of the crankshaft according to embodiment 1, and FIG. 4B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 4A. [FIG. 5] FIG. 5A is a side view of another crankshaft according to embodiment 1, and FIG. 5B is a sectional projection view along a line A-A of the other crankshaft shown in FIG. 5A. [FIG. 6] FIG. 6A is a side view of a crankshaft according to embodiment 2, and FIG. 6B is a top view of the crankshaft according to embodiment 2. [FIG. 7] FIG. 7A is a side view of the crankshaft according to embodiment 2, and FIG. 7B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 7A. [FIG. 8] FIG. 8A is a side view of a crankshaft according to embodiment 3, and FIG. 8B is a top view of the crankshaft according to embodiment 3. [FIG. 9] FIG. 9A is a side view of the crankshaft according to embodiment 3, and FIG. 9B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 9A. [FIG. 10] FIG. 10A is a side view of a crankshaft according to embodiment 4, and FIG. 10B is a top view of the crankshaft according to embodiment 4. [FIG. 11] FIG. 11A is a side view of the crankshaft according to embodiment 4, and FIG. 11B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 11A [FIG. 12] FIG. 12A is a side view of a crankshaft according to embodiment 5, and FIG. 12B is a top view of the crankshaft according to embodiment 3. [FIG. 13] FIG. 13A is a side view of the crankshaft according to embodiment 5, and FIG. 13B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 13A. [FIG. 14] FIG. 14A is a side view of another crankshaft according to embodiment 5, and FIG. 14B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 14A. [FIG. 15] FIG. 15 is a partially enlarged view of a compression drive portion of a scroll compressor according to embodiment 6. [FIG. 16] FIG. 16 shows a configuration of a balancer portion in an X-Y coordinate system in FIG. 9A. [FIG. 17] FIG. 17 shows a configuration of a balancer portion in the X-Y coordinate system in FIG. 11A. [FIG. 18] FIG. 18A shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, FIG. 18B shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, FIG. 18C shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, and FIG. 18D shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4. [FIG. 19] FIG. 19A is a side view of a crankshaft according to embodiment 7, and FIG. 19B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 19A. [FIG. 20] FIG. 20A is a side view of a crankshaft according to embodiment 8, and FIG. 20B is a top view of the crankshaft according to embodiment 8. [FIG. 21] FIG. 21 is a sectional view of a scroll compressor according to embodiment 8. [FIG. 22] FIG. 22 is a partial sectional view of the scroll compressor according to embodiment 8. [FIG. 23] FIG. 23 is a partial sectional view of another scroll compressor according to embodiment 8. [FIG. 24] FIG. 24 shows another configuration of the balancer portion in the X-Y coordinate system of the scroll compressor according to embodiment 1. [FIG. 25] FIG. 25 is a sectional view showing the shape of a member before the balancer portion of the scroll compressor according to embodiment 4 is formed. [FIG. 26] FIG. 26A shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, FIG. 26B shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, FIG. 26C shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4, and FIG. 26D shows another configuration of the balancer portion in the X-Y coordinate system according to embodiment 4. DESCRIPTION OF EMBODIMENTS

[0009] Embodiment 1 Embodiment 1 will be described with reference to the drawings. FIG. 1 is a perspective view of a scroll compressor 100 of a vertical type. FIG. 2 is a sectional view of the scroll compressor 100 of the vertical type, wherein a U-side denotes the upper side and an L-side denotes the lower side. U-side and L-side in the other drawings denote the U-side and the L-side in FIG. 2. This relationship also applies to the subsequent embodiments, and thus, description thereof will be omitted as appropriate.

[0010] As shown in FIG. 1 and FIG. 2, the scroll compressor 100 includes, as major structures: a shell 1 composed of a middle shell 11, an upper shell 12, and a lower shell 13; a crankshaft 6 supported by a bearing of the middle shell 11; a drive portion 4 for rotationally driving the crankshaft 6; and a compression drive portion 3 provided with a fixed scroll 31 and an orbiting scroll 32.

[0011] An outline of operation of the scroll compressor 100 having such a configuration will be described. Through operation of the drive portion 4, the crankshaft 6 is rotated and a refrigerant flows through a first frame 2 into the compression drive portion 3. Here, the orbiting scroll 32 provided to an eccentric shaft portion 62 of the crankshaft 6 swings, whereby the refrigerant is compressed in a compression chamber 34. The compressed refrigerant flows through the fixed scroll 31 into a discharge pipe 15.

[0012] A balancer cover 301 is provided to a later-described balancer portion 61B provided between a main shaft portion 61 and the first frame 2 disposed on the L-side of the orbiting scroll 32. The balancer cover 301 has a function of storing a refrigerant oil coming up in the scroll compressor 100 through a later-described oil passage 60 together with the refrigerant, and suppressing exit of the refrigerant oil to the outside of the scroll compressor 100, thereby suppressing decrease of the heat exchange ability of a heat exchanger connected to the scroll compressor 100. The balancer cover 301 is installed by being fixed to the first frame 2 with a bolt or the like.

[0013] FIG. 3A and FIG. 3B show the crankshaft 6 including the balancer portion 61B formed as an integrally-formed object for decreasing a non-equilibrium force associated with rotation of the crankshaft 6 addressed by the present disclosure. FIG. 3A is a side view of the crankshaft according to embodiment 1. FIG. 3B is a top view of the crankshaft according to embodiment 1, viewed from the U-side (arrow Z) direction in FIG. 3A. FIG. 4A is an enlarged view of the balancer portion 61B in FIG. 3A. FIG. 4B is a sectional projection view along a line A-A in FIG. 4A.

[0014] As shown in FIG. 4, in a coordinate system at a plane vertical to a rotation axis 6CL of the crankshaft 6, a line on a horizontal plane including the rotation axis 6CL is defined as an X-axis, a vertical center line of the crankshaft 6 orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis 6CL where the X-axis and the Y-axis cross each other is defined as an origin C. As a weight portion 612, the balancer portion 61B has a balancerside weight portion 612A and a counter-balancer-side weight portion 612B. The balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are provided so as to be continuous with a plane including the rotation axis 6CL of the crankshaft 6.

[0015] In the X-Y coordinate system defined as above, the balancer-side weight portion 612A is formed in the first quadrant and the second quadrant, and the counter-balancer side weight portion 612B is formed in the third quadrant and the fourth quadrant. In the present embodiment 1 and the other embodiments, the relationship between the X-axis, the Y-axis, and the origin C, and the crankshaft 6 and the rotation axis 6CL; and the relationship between the balancerside weight portion 612A and the counter-balancer-side weight portion 612B are the same. Therefore, description of the relationships will be omitted as appropriate. Indication of the first quadrant, the second quadrant, the third quadrant, and the fourth quadrant are provided only in FIG. 4B, and are not provided in the other drawings.

[0016] In FIG. 3A, the crankshaft 6 includes the oil passage 60, the main shaft portion 61, and the eccentric shaft portion 62. The main shaft portion 61 is a major portion of the crankshaft 6, and is disposed such that the rotation axis 6CL matches the axial center line of the middle shell 11 shown in FIG. 2. The eccentric shaft portion 62 is provided on the U-side of the crankshaft 6 such that an eccentric axis 62CL is eccentric with respect to the rotation axis 6CL of the main shaft portion 61.

[0017] The oil passage 60 is provided so as to penetrate the crankshaft 6 from an L-side end to a U-side end. In FIG. 3A, the oil passage 60 is provided along the rotation axis 6CL of the crankshaft 6. However, not limited thereto, the oil passage 60 may be provided on the lower side with respect to the X-axis in FIG. 4B.

[0018] In the main shaft portion 61, from the U-side in sequential order, a main bearing portion 61A, the balancer portion 61B, a rotor shrink fit portion 61C, and a sub bearing portion 61D are provided. In the rotor shrink fit portion 61C, a rotor 4A of the drive portion 4 shown in FIG. 2 is provided. The main bearing portion 61A is inserted in a bearing portion 2A of the first frame 2. The sub bearing portion 61D is inserted in a sub bearing portion 5A of a second frame 5. As shown in FIG. 2, between the bearing portion 2A of the first frame 2 and the main bearing portion 61A of the crankshaft 6, a sleeve bearing 65 driven according to rotation of the crankshaft 6 is provided.

[0019] As shown in FIG. 4B, in the weight portion 612 forming the balancer portion 61B, the balancer-side weight portion 612A having a smooth semicircular shape that has a radius Rlmax is provided over the first quadrant and the second quadrant of the X-Y coordinate system, and the counter-balancer-side weight portion 612B having a smooth semicircular shape that has a radius R2max is provided over the third quadrant and the fourth quadrant. That is, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are provided so as to be continuous with each other along the Y-axis. Due to the setting of the radius Rlmax >the radius R2max, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are distinguished from each other. That is, according to the relationship in magnitude of the weight and the position of the center of gravity, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are defined. In the case of the configuration shown in FIG. 4, the radius Rlmax is the maximum distance of the balancer-side weight portion 612A from the origin C, and the radius R2max is the maximum distance of the counter-balancer-side weight portion 612B from the origin C.

[0020] Here, a first center of gravity 61G of the balancer-side weight portion 612A and a second center of gravity 62C of the counter-balancer-side weight portion 612B are shown. The reason why the first center of gravity 61G of the balancer-side weight portion 612A and the second center of gravity 62C of the counter-balancer-side weight portion 612B are present on the Y-axis is that the weight portion 612 is symmetrical with respect to the Y-axis and has a smooth semicircular shape. A flange portion 611 provided in the balancer portion 61B will be described later.

[0021] The planar shapes and dimensions of the balancerside weight portion 612A and the counter-balancer-side weight portion 612B described above are set in accordance with the constitution (capacity, dimension, rotational speed, and the like) of the scroll compressor 100. In addition, a smooth semicircular shape is not necessarily adopted. What is important as a balancer is that the product of "the distance (this corresponds to the distance from the origin C on the coordinates on the X-Y-axes), from the rotation axis 6CL, of the center of gravity of the balancer," and "the weight of the balancer" is large. When this distance is increased, the weight can be reduced, but the special dimensions are increased.

[0022] In the present embodiment 1, in order to realize the relationship of "the weight of the balancer-side weight portion >the weight of the counter-balancer-side weight portion", the weight ratio between the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B is set to be 4:1, for example. That is, the area ratio in at least one cross section being a cross section vertical to the rotation axis 6CL is set to be 4:1, for example. That is, the area in a cross section vertical to the rotation axis 6CL has a relationship of "the area of the balancer-side weight portion 612A >the area of the counter-balancer-side weight portion 612B". Accordingly, the relationship of "the weight of the balancer-side weight portion 612A >the weight of the counter-balancer-side weight portion 612B" can be easily obtained.

[0023] Next, the reason why "max" as, for example, in the radius Rlmax and the radius R2max is used in FIG. 4B, will be described. The radius Rlmax of the balancer-side weight portion 612A and the radius R2max of the counter-balancer-side weight portion 612B each represent a smooth arc shape. However, not limited thereto, for example, a shape of an arc shape in which the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B partially have an elliptical shape or a protrusion / recess shape may be adopted (an example of this will be described later with reference to FIG. 24) . In that case, the radius Rlmax denotes the part that corresponds to the maximum distance of the balancer-side weight portion 612A, and the radius R2max denotes the part that corresponds to the maximum distance of the counterbalancer-side weight portion 612B.

[0024] Thus, "max" is used, taking such a shape of an arc shape having an elliptical shape or a protrusion / recess shape into consideration. It should be noted that, regarding the arc shape of the balancer portion 61B, adoptability of a shape of an arc shape that partially has an elliptical shape or a protrusion / recess shape also applies to the subsequent embodiments as well, and thus, description thereof will be omitted as appropriate. Here, a relationship with 1 / 2 of a diameter d, i.e., d / 2, of the main bearing portion 61A is the radius R2max>d / 2. However, in this embodiment 1, the radius R2max of the balancer portion 61B is set to be larger.

[0025] As shown in FIG. 3 and FIG. 4, the balancer portion 61B is composed of: the flange portion 611 of which the planar shape is a semicircular shape; and the weight portion 612 having a shape in which the balancer-side weight portion 612A having a semicircular shape that has the radius Rlmax and the counter-balancer-side weight portion 612B having a semicircular shape that has the radius R2max are continuous with each other. In the flange portion 611 shown in FIG. 4, a distance 611Rmin from the rotation axis 6CL to the outermost diameter is set to be larger than d / 2 of the main bearing portion 61A. That is, there is a relationship of the distance 611Rmin>d / 2. Although the relationship between the distance 611Rmin and the radius Rlmax of the balancer-side weight portion 612A is the distance 611Rmin<the radius Rlmax, the present disclosure is not limited thereto.

[0026] The flange portion 611 described above has a function of supporting, in the axial direction, the bearing provided between the crankshaft 6 and the second frame 5.

[0027] Other examples will be described with reference to the drawings. FIG. 5A is a side view of another crankshaft according to embodiment 1. FIG. 5B is a sectional projection view along a line A-A of the other crankshaft shown in FIG. 5A. In FIG. 5B, the balancer-side weight portion 612A has a semicircular shape that has a linear portion LC1 in a perpendicular direction at a predetermined distance LI from the Y-axis in the first quadrant. The counter-balancer-side weight portion 612B has a semicircular shape that has a linear portion LC2 in the Y-axis direction at a predetermined distance L2 from the Y-axis in the fourth quadrant. It should be noted that "predetermined" means "a value or thing set in advance", and this also applies to the description below. Thus, description thereof will be omitted as appropriate. The second center of gravity 62C of the counter-balancer-side weight portion 612B and the first center of gravity 61G of the balancer-side weight portion 612A form an angle 0 about the origin C.

[0028] The linear portion LC1 is a side formed in parallel to the Y-axis. In the present disclosure, a "side" denotes a "part formed in a linear shape". This content also applies to the subsequent embodiments, and thus, description thereof will be omitted as appropriate. The linear portion LC2 formed in the counter-balancer-side weight portion 612B corresponds to one of first sides formed in either one or both of the third quadrant and the fourth quadrant of the X-Y coordinate system. Here, the linear portion LC2 corresponds to the first side formed in the fourth quadrant. The linear portion LC2 is formed in parallel to the Y-axis.

[0029] The above-mentioned "parallel" includes "exactly parallel" and naturally includes "parallel" that includes an error range in processing. This definition of "parallel" also applies to the subsequent embodiments, and thus, description thereof will be omitted as appropriate.

[0030] In FIG. 5B, the linear portion LC1 is present in the first quadrant and the linear portion LC2 is present in the fourth quadrant, but may be respectively formed in the balancer portion 61B provided in the second quadrant and the third quadrant. A combination of these shapes may be adopted. Regarding the planar shape of the flange portion 611, a semicircular shape is adopted in consideration of processability, but is not limited to a semicircular shape since the flange portion 611 is for supporting the sleeve bearing 65.

[0031] Next, the positional relationship between the first center of gravity 61G of the balancer-side weight portion 612A and the second center of gravity 62C of the counter-balancer-side weight portion 612B will be described with reference to FIG. 5B. This also applies to a case where the planar shape of the balancer portion 61B is not a smooth semicircular shape as described above, and description thereof will be given below. In the X-Y coordinate system that passes through the first center of gravity 61G of the balancer-side weight portion 612A and that is vertical to the rotation axis 6CL of the crankshaft 6, the angle 0 between a line passing through the origin C and the first center of gravity 61G of the balancer-side weight portion 612A, and a line passing through the origin C and the second center of gravity 62C of the counter-balancer-side weight portion 612B is set to be preferably 180 degrees, and at least not less than 90 degrees and not greater than 270 degrees. FIG. 5B shows an example of the angle 0 above.

[0032] In FIG. 4B, when, in the X-Y coordinate system that passes through the first center of gravity 61G of the balancer-side weight portion 612A of the balancer portion 61B and that is perpendicular to the rotation axis 6CL of the crankshaft 6, the X-Y coordinate system is divided into two in a vertical manner, i.e., by the X-axis in this case, with respect to a line that connects the first center of gravity 61G of the balancer-side weight portion 612A and a point passing through the rotation axis 6CL, the part on the side where the first center of gravity 61G is present is the balancer-side weight portion 612A, and the part on the side where the second center of gravity 62C as the other one is the counter-balancer-side weight portion 612B. In a cross-sectional shape of the balancer portion 61B of the crankshaft 6 in the X-Y coordinate system, with respect to the maximum distance from the origin C, when the radius of the arc of the balancer-side weight portion 612A is defined as Rlmax, and the radius of the arc of the counter-balancer-side weight portion 612B is defined as R2max, the former is set to be larger . the radius Rlmaxkthe radius R2max

[0033] On the L-side of the crankshaft 6 shown in FIG. 2, a balancer 66 is provided so as to cancel imbalance caused by swing of the orbiting scroll 32. The crankshaft 6 is integrally formed in a jointless manner with the same forming material by using, as a material, a forged article or a cast article of steel, or an alloy produced by sintering a metal powder. The entirety of the crankshaft 6 including the balancer portion 61B provided as an integrally-formed object is finished to have a predetermined shape and dimensions by machining, e.g., N / C (Numerical Control) processing. The balancer portion 61B may be intentionally subjected to additional processing in order to improve balance in the scroll compressor 100.

[0034] In the scroll compressor 100 including the crankshaft 6 having the above configuration, the balancer portion 61B provided to the crankshaft 6 rotates, whereby the centrifugal force of the orbiting scroll 32 swinging in an eccentric manner is canceled, and burning and wear of the bearing are prevented. Since the balancer portion 61B is provided, as an integrally-formed object, to the crankshaft 6, the ring portion for shrink fit can be eliminated. Therefore, the weight portion 612 can be downsized and the rigidity of the crankshaft 6 is improved.

[0035] Since this configuration is adopted, attachment of a balance weight is not necessary, and thus, assembling work of the scroll compressor 100 can be performed 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, reliability of the scroll compressor 100 is improved, the compression amount of the refrigerant can be increased, and the rotational speed at use can be increased. Further, as shown in FIG. 2, the sleeve bearing 65 can be provided between a bearing portion 22 of the first frame 2 and the main bearing portion 61A of the crankshaft 6, whereby the reliability is more improved.

[0036] Since the entirety of the crankshaft 6 including the balancer portion 61B is subjected to machining, the weight and the center of gravity can be highly accurately controlled, and the centrifugal force of the orbiting scroll 32 can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved.

[0037] The balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are provided so as to be continuous with each other in the X-Y coordinate system including the rotation axis 6CL of the crankshaft 6, i.e., here, along the Y-axis. Therefore, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B can be formed symmetrically, for example, in such a case as shown in FIG. 4, with respect to the X-Y coordinate system, whereby control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll 32 can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved.

[0038] With respect to the balancer portion 61B, the flange portion 611, the balancer-side weight portion 612A, and the counter-balancer-side weight portion 612B each have a semicircular shape having the origin C as a center, and thus, can be processed simultaneously with another part of the crankshaft 6. Since simultaneous processing can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll 32 can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved.

[0039] Since the distance 611Rmin from the rotation axis 6CL to the outermost diameter is formed so as to be larger than d / 2 of the main bearing portion 61A, the diameter of the balancer portion 61B is increased, the rigidity can be improved, and the reliability can be improved.

[0040] As shown in FIG. 24, it is also conceivable that a part of the outer shape of the counter-balancer-side weight portion 612B is formed in an elliptical shape 612BB. Then, a side S22 and a side S23 are formed. The side S22 and the side S23 formed in the counter-balancer-side weight portion 612B correspond to one of first sides formed in either one or both of the third quadrant and the fourth quadrant of the X-Y coordinate system. The side S22 corresponds to the first side formed in the fourth quadrant and the side S23 corresponds to the first side formed in the third quadrant. The side S22 and the side S23 are formed so as to be parallel to the Y-axis. In this manner, when the elliptical shape 612BB or a protrusion / recess shape (a shape having protrusions and recesses on the surface) is used, the total weight of the balancer portion 61B can be reduced, and the weight portion 612 can be downsized.

[0041] The angle 0 between the line passing through the origin C and the first center of gravity 61G of the balancerside weight portion 612A and the line passing through the origin C and the second center of gravity 62C of the counterbalancer-side weight portion 612B is preferably 180 degrees, and at least not less than 90 degrees and not greater than 270 degrees. Accordingly, the weight of the counter-balancer-side weight portion 612B can be reduced and the weight portion 612 can be downsized. Since the centrifugal force of the orbiting scroll 32 can be highly accurately canceled, vibration is reduced, and the reliability can be improved.

[0042] In the description above, for simplification, the second center of gravity 62C of the counter-balancer-side weight portion 612B is present without fail in the X-Y coordinate system that passes through the first center of gravity 61G of the balancer-side weight portion 612A and that is vertical to the rotation axis 6CL of the crankshaft 6. However, not limited thereto, in a case where the second center of gravity 62C of the counter-balancer-side weight portion 612B is not present in the X-Y coordinate system, a point, of the second center of gravity 62C, transcribed along the rotation axis 6CL direction onto the X-Y coordinate system may be considered as an alternative of the second center of gravity 62C. This matter also applies to the subsequent embodiments, and thus, description thereof will be omitted as appropriate.

[0043] The scroll compressor of embodiment 1 having the configuration as described above includes: a crankshaft supported by a bearing fixed to a shell; a drive portion for the crankshaft; an orbiting scroll provided to an eccentric shaft portion of the crankshaft; and a fixed scroll provided to the shell, and a main shaft portion of the crankshaft is provided with a balancer portion that is formed as an integrally-formed object and that decreases a non-equilibrium force associated with rotation of the crankshaft. Therefore, the non-equilibrium force associated with rotation of the crankshaft can be decreased by the balancer portion, and thus, the scroll compressor of which assembling work is easy and that is small in size can be realized.

[0044] Further, according to the scroll compressor of embodiment 1, the balancer portion is composed of a balancer-side weight portion and a counter-balancer-side weight portion, and the balancer-side weight portion and the counterbalancer-side weight portion are provided so as to be continuous with a plane including a rotation axis of the crankshaft, and in order to realize a relationship of a weight of the balancer-side weight portion >a weight of the counter-balancer-side weight portion, an area in at least one cross section being a cross section vertical to the rotation axis has a relationship of an area of the balancer-side weight portion >an area of the counter-balancer-side weight portion. Therefore, simply by realizing the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion, it is possible to obtain, in a simple manner, a balancer portion that can decrease the non-equilibrium force associated with rotation of the crankshaft.

[0045] Further, according to the scroll compressor of embodiment 1, in a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin, the counter-balancer-side weight portion has a first side in either one or both of a third quadrant and a fourth quadrant of the coordinate system. Therefore, by forming the first side, it is possible to obtain, in a simple manner, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion.

[0046] Further, according to the scroll compressor of embodiment 1, the first side is formed as a side parallel to the Y-axis . Therefore, processing by a general-purpose machine such as a two-axis lathe can be performed. Since simultaneous processing with another part can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll can be highly accurately canceled, and thus, vibration is reduced, and the reliability can be improved. Since processing by a general-purpose machine can be performed, capital investment is reduced, whereby low cost can be realized.

[0047] Further, according to the scroll compressor of embodiment 1, the balancer-side weight portion has a side that is parallel to the Y-axis and that has a distance LI from the Y-axis, in either one of a first quadrant and a second quadrant of the coordinate system, and the first side of the counter-balancer-side weight portion has a first side that is parallel to the Y-axis and that has a distance L2 from the Y-axis, a relationship of the distance Ll>the distance L2 is realized, and the parallel side and the parallel first 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 counterbalancer-side weight portion can be obtained in a simple and assured manner. Further, processing by a general-purpose machine such as a two-axis lathe can be performed. Since simultaneous processing with another part can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll can be highly accurately canceled, and thus, vibration is reduced, and the reliability can be improved. Since processing by a general-purpose machine can be performed, capital investment is reduced, whereby low cost can be realized.

[0048] Further, according to the scroll compressor of embodiment 1, in a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin, the balancer-side weight portion and the counter-balancer-side weight portion each have a semicircular shape having the origin as a center, and a maximum distance of the semicircular shape from the origin is formed so as to have a relationship of a maximum distance of the balancer-side weight portion >a maximum distance of the counter-balancer-side weight portion. Therefore, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion can be obtained in a simple and assured manner.

[0049] Further, according to the scroll compressor of embodiment 1, a part of an outer shape of the counter-balancer-side weight portion is formed in an elliptical shape or a protrusion / recess shape. Therefore, the balancer portion can be reduced in the total weight and can be downsized.

[0050] Further, according to the scroll compressor of embodiment 1, with reference to the origin as a center, an angle between a line passing through the origin and a first center of gravity of the balancer-side weight portion and a line passing through the origin and a second center of gravity of the counter-balancer-side weight portion is not less than 90 degrees and not greater than 270 degrees. Therefore, the counter-balancer-side weight portion can be reduced in weight and can be downsized. Since the centrifugal force of the orbiting scroll can be highly accurately canceled, vibration is reduced, and the reliability can be improved.

[0051] Further, according to the scroll compressor of embodiment 1, the balancer portion is provided with a flange portion continuous, in an axial direction, with the balancerside weight portion. Therefore, the balancer portion can be easily supported by the flange portion to another part.

[0052] Further, according to the scroll compressor of embodiment 1, the entire shape of the crankshaft is formed by machining. Therefore, control of the position of the center of gravity is easy, and the centrifugal force of the orbiting scroll can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved.

[0053] In the following embodiments as well, similar to the present embodiment 1, the main shaft portion of the crankshaft is provided with a balancer portion that is formed as an integrally-formed object and that decreases a non-equilibrium force associated with rotation of the crankshaft, and in the X-Y coordinate system, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion is realized. Therefore, the description thereof will be omitted as appropriate.

[0054] Embodiment 2 Next, a crankshaft 6 of embodiment 2 will be described with reference to the drawings. FIG. 6A is a side view of the crankshaft according to embodiment 2. FIG. 6B is a top view of the crankshaft according to embodiment 2, viewed from the U-side (arrow Z) direction in FIG. 6A. FIG. 7A shows an enlarged view of the balancer portion 61B in FIG. 6A. FIG. 7B shows a sectional projection view along a line A-A in FIG. 6A. In the drawings, parts similar to those in embodiment 1 above will be denoted by the same reference characters, and description thereof is omitted.

[0055] As shown in the drawings, in this configuration, the balancer portion 61B is not provided with the flange portion 611 shown in FIG. 3A and FIG. 3B of embodiment 1 described above. That is, the balancer portion 61B is provided with the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B. Other than this, embodiment 2 is the same as embodiment 1. With this configuration, effects of further downsizing and reduction in weight are exhibited in addition to those in embodiment 1. With the configuration of embodiment 2, the sleeve bearing 65 cannot be supported. Therefore, as an alternative, the bearing portion 2A of the first frame 2 is processed or a bearing is installed by press fitting or the like, whereby a bearing corresponding to the main bearing portion 61A is realized.

[0056] In the case of the shape shown in FIG. 7B, the shape can be formed by forging or casting, and thus, can be formed without performing cutting. This matter also applies to the case shown in FIG. 4B of embodiment 1 described above. In the case of FIG. 5B of embodiment 1 described above, from the state shown in FIG. 4B, the linear portion LC1 and the linear portion LC2 can be formed by cutting.

[0057] According to the scroll compressor of embodiment 2 having the configuration as described above, effects similar to those of the embodiment described above can be exhibited. In addition, since the flange portion is not provided, downsizing and reduction in weight can be realized.

[0058] Embodiment 3 Next, a crankshaft 6 of embodiment 3 will be described with reference to the drawings. FIG. 8A is a side view of the crankshaft according to embodiment 3. FIG. 8B is a top view of the crankshaft according to embodiment 3, viewed from the U-side (arrow Z) direction in FIG. 8A. FIG. 9A shows an enlarged view of the balancer portion 61B in FIG. 8A. FIG. 9B shows a sectional projection view along a line A-A in FIG. 9A. With reference to FIG. 16, a first side formed in either one or both of the third quadrant and the fourth quadrant of the X-Y coordinate system will be described. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted.

[0059] As shown in FIG. 9, the planar shape of the counter-balancer-side weight portion 612B is a rectangular shape formed by linear portions 612S. The rectangular shape of the counter-balancer-side weight portion 612B is a shape in which linear portions 612S forming a width W1 are connected with each other, at the position of a distance H3 from the X-axis. The intersection of the distance H3 and the width W1 crosses the circumference having the radius R2max, without being limited thereto. The linear portion 612S serving as the lower surface of the rectangular shape is parallel to the X-axis. The balancer-side weight portion 612A has the same shape as that shown in FIG. 4 in embodiment 1. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has effects similar to those in embodiment 1.

[0060] Next, a first side and a second side formed in the counter-balancer-side weight portion 612B in embodiment 3 will be described with reference to FIG. 16. First, the first side denotes a side (linear portion) formed in either one or both of the third quadrant and the fourth quadrant of the coordinate system in the counter-balancer-side weight portion. The second side denotes a side (linear portion) contiguous with the first side of the balancer portion 61B, in the coordinate system at a plane vertical to the rotation axis of the crankshaft. The relationship between the first side and the second side also applies to the subsequent embodiments, and thus, description thereof will be omitted as appropriate.

[0061] As shown in FIG. 16, the linear portions 612S of the counter-balancer-side weight portion 612B are defined as a side Sil, a side S12, and a side S13, respectively. Therefore, one of the side Sil, the side S12, and the side S13 corresponds to the first side formed in either one or both of the third quadrant and the fourth quadrant at the coordinate system in the counter-balancer-side weight portion 612B. When the side Sil is defined as the first side, the side S12 corresponds to the side contiguous with the side Sil, i.e., the second side.

[0062] When the side S12 is defined as the first side, both of the side S12 and the side S13 correspond to the side contiguous with the side S12, i.e., the second side. The side Sil is formed in the fourth quadrant of the X-Y coordinate system, and is formed in parallel to the Y-axis. The side S12 is formed so as to be continuous in both of the third quadrant and the fourth quadrant of the X-Y coordinate system, and is formed in parallel to the X-axis. The side S13 is formed in the third quadrant of the X-Y coordinate system, and is formed in parallel to the Y-axis.

[0063] Since the side S12 parallel to the X-axis is provided, simultaneous processing with another part of the crankshaft 6 by a general-purpose machine such as a two-axis lathe can be performed. Since simultaneous processing can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll 32 can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved. Since processing by a general-purpose machine can be performed, capital investment is reduced, and inexpensive production can be realized.

[0064] The counter-balancer-side weight portion 612B is formed in a shape provided with the sides Sil, S13 that have the distance H3 from the X-axis in the X-Y coordinate system. Therefore, the following effects are exhibited: without significant impairment of the rigidity of the crankshaft 6, the weight of the counter-balancer-side weight portion 612B can be reduced; the weight portion 612 can be downsized; and larger centrifugal force cancellation is enabled. In addition, an effect that the linearity enables easy processing by, for example, a cutting tool such as an end mill, is exhibited.

[0065] In the case of the shape shown in FIG. 16, from the state shown in FIG. 7B of embodiment 2 described above, the side Sil, the side S12, and the side S13 can be formed by cutting.

[0066] According to the scroll compressor of embodiment 3 having the configuration as described above, effects similar to those of each embodiment described above are exhibited. In addition, in the coordinate system at the plane vertical to the rotation axis of the crankshaft, the balancer portion has a second side contiguous with the first side. Therefore, the relationship of the area of the balancer-side weight portion >the area of the counterbalancer-side weight portion can be obtained in a simple and assured manner.

[0067] Further, according to the scroll compressor of embodiment 3, the balancer-side weight portion has a semicircular shape having the origin as a center, and the counter-balancer-side weight portion is formed in a polygonal shape. Therefore, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion can be obtained in a simple and assured manner.

[0068] Further, according to the scroll compressor of embodiment 3, when a maximum distance of the semicircular shape of the balancer-side weight portion is defined as Rlmax, and a maximum distance in the X-axis direction of the counter-balancer-side weight portion is defined as Wl, the balancer-side weight portion and the counterbalancer-side weight portion are formed so as to have a relationship of Rlmax>Wl. Therefore, the relationship of the area of the balancer-side weight portion >the area of the counterbalancer-side weight portion can be obtained in a simpler and further assured manner.

[0069] Embodiment 4 Next, a crankshaft 6 of embodiment 4 will be described with reference to the drawings. FIG. 10A is a side view of the crankshaft according to embodiment 4. FIG. 10B is a top view of the crankshaft according to embodiment 4, viewed from the U-side (arrow Z) direction in FIG. 10A. FIG. 11A shows an enlarged view of the balancer portion 61B in FIG. 10A. FIG. 11B shows a sectional projection view along a line A-A in FIG. 11A. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted.

[0070] As shown in FIG. 11, the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B are formed so as to have a substantially inversed protrusion shape as a whole. The balancer-side weight portion 612A is in a substantially mushroom shape that has: an arc having the radius Rlmax; and the width W1 parallel to the X-axis up to a position separated by a predetermined distance Hl from the X-axis. The counter-balancer-side weight portion 612B has a shape in which: the W1 is extended up to a position at a distance H2 from the X-axis; and a straight line parallel to the X-axis and having a width W2 at the position of the predetermined distance H3 from the X-axis is connected, by oblique lines, to the W1 at the position of the distance H2.

[0071] The linear portions 612S are provided on the counter-balancer-side weight portion 612B side of the substantially mushroom shape. With reference to FIG. 17 described later, the intersection of a side S18 and a side S17, the intersection of the side S17 and a side S16, the intersection of the side S16 and a side S15, and the intersection of the side S15 and a side S14 cross the circumference having the radius R2max shown in FIG. 11B. However, the present disclosure is not limited thereto. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has effects similar to those of embodiment 1.

[0072] Next, a first side and a second side in embodiment 4 will be described with reference to FIG. 17. In the drawing, the respective sides are defined as the side S14, the side S15, the side S16, the side S17, the side S18, a side Vil, and a side V14. Therefore, one of the side S14, the side S15, the side S16, the side S17, and the side S18 corresponds to the first side formed in either one or both of the third quadrant and the fourth quadrant of the coordinate system in the counter-balancer-side weight portion 612B. The side Vil and the side V14 correspond to the second side contiguous with the first side.

[0073] When the side S16 is defined as the first side, the side S15 and the side S17 correspond to the sides contiguous with the side S16, i.e., the second side. When the side S14 is defined as the first side, the side S15 and the side Vil correspond to the sides contiguous with the side S14, i.e., the second side. When the side S18 is defined as the first side, the side S17 and the side V14 correspond to the sides contiguous with the side S18, i.e., the second side. When the side S15 is defined as the first side, the side S14 and the side S16 correspond to the sides contiguous with the side S15, i.e., the second side. When the side S17 is defined as the first side, the side S18 and the side S16 correspond to the sides contiguous with the side S17, i.e., the second side .

[0074] The side S14 is formed so as to be continuous in both of the first quadrant and the fourth quadrant of the X-Y coordinate system, and is formed in parallel to the Y-axis. The side S15 is formed in the fourth quadrant of the X-Y coordinate system.

[0075] The side S16 is formed so as to be continuous in both of the third quadrant and the fourth quadrant of the X-Y coordinate system, and is formed in parallel to the X-axis. The side S17 is formed in the third quadrant of the X-Y coordinate system. The side S18 is formed so as to be continuous in both of the second quadrant and the third quadrant of the X-Y coordinate system, and is formed in parallel to the Y-axis. The side Vil is formed in the first quadrant of the X-Y coordinate system, and crosses the side S14 at a right angle, but the angle is not limited to the right angle. The side V14 is formed in the second quadrant of the X-Y coordinate system, and crosses the side S18 at a right angle, but the angle is not limited to the right angle.

[0076] The counter-balancer-side weight portion 612B has a shape in which: the width W1 is extended up to the position at the distance H2 from the X-axis; and a straight line parallel to the X-axis and having the width W2 at the position of the predetermined distance H3 from the X-axis is connected, by oblique lines, to the width W1 at the position of the distance H2. Accordingly, the weight of the counter balancer-side weight portion 612B can be reduced, and the weight portion 612 can be downsized. Further, larger cancellation is enabled.

[0077] The counter-balancer-side weight portion 612B is formed so as to include (a part of) the side S14 and (a part of) the side S18 which are the linear portions 612S having a length of the distance H2 from the X-axis in the X-Y coordinate system, and (a part of) the side S14 and (a part of) the side S18 which are the linear portions 612S having the width W1. Therefore, the following effects are exhibited: without significant impairment of the rigidity of the crankshaft 6, the weight of the counter-balancer-side weight portion 612B can be further reduced; the weight portion 612 can be further downsized; and still larger centrifugal force cancellation is enabled. In addition, the linearity enables easy processing by, for example, a cutting tool such as an end mill.

[0078] The counter-balancer-side weight portion 612B is formed so as to include (a part of) the side S14 and (a part of) the side S18 which have the distance H2 in the X-Y coordinate system, and the side S15 or the side S17 contiguous with the side S14 or the side S18, and the side S16 parallel to the X-axis. Therefore, the following effects are exhibited: without significant impairment of the rigidity of the crankshaft 6, the weight of the counter-balancer-side weight portion 612B can be further reduced; the weight portion 612 can be further downsized; and still larger centrifugal force cancellation is enabled.

[0079] In the case of the shape shown in FIG. 17, an effect that the linearity of the side S14s to S18 enables easy processing by, for example, a cutting tool such as an end mill from the state shown in FIG. 7B of embodiment 2 described above, is exhibited. It is preferable that the distance Hl and the distance H2 are set to be the same length. When the distance Hl=the distance H2, simultaneous processing with another part of the crankshaft 6 by a general-purpose machine such as a two-axis lathe can be performed. Since simultaneous processing can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll 32 can be highly accurately canceled. Therefore, vibration is reduced, and the reliability can be improved. Since processing by a general-purpose machine can be performed, investment is reduced, and inexpensive production can be realized.

[0080] Here, the first side, the second side, and still another example will be described with reference to FIG. 18, FIG. 25, and FIG. 26. Similar to each embodiment described above, FIG. 18 and FIG. 26 each show only the shape on the plane of the balancer portion 61B in the X-Y coordinate system, and does not show the other parts. Similar to each embodiment described above, FIG. 25 is a sectional view showing a configuration of the member before the balancer portion 61B is formed in the X-Y coordinate system, and shows only the planar shape.

[0081] First, when each balancer portion 61B as shown in FIG. 18 and FIG. 26 is to be obtained, in the present disclosure, for example, the balancer portion 61B of the present disclosure is produced, by cutting, from a cylindrical member formed by forging or casting. Therefore, before cutting, as shown in FIG. 25, the member has a circular shape 600 in the X-Y coordinate system. Then, cutting is performed from the state of the circular shape 600 to form the balancer portion 61B. This case will be described.

[0082] With reference to FIG. 18A, in the counterbalancer-side weight portion 612B, a side S19 as the first side continuous in the third quadrant and the fourth quadrant is formed. In this example, no second side contiguous with the first side is formed. FIG. 18B shows an example in which no first side and no second side are formed. In the balancer-side weight portion 612A, a side V15 is formed in the first quadrant, and a side V16 is formed in the second quadrant.

[0083] In FIG. 18C, a side S20 as the first side is formed in the fourth quadrant of the counter-balancer-side weight portion 612B. A side contiguous with the side S20 is formed as a side V17 in the first quadrant of the balancer-side weight portion 612A. Therefore, the side V17 corresponds to the second side. In FIG. 18D, a side S21 as the first side is formed continuously from the fourth quadrant of the counter-balancer-side weight portion 612B to the balancerside weight portion 612A.

[0084] In FIG. 26A, a side S24 as the first side continuous in the third quadrant and the fourth quadrant of the counter-balancer-side weight portion 612B is formed. In this example, no second side contiguous with the first side is formed. In FIG. 26B, a side S25 as the first side is formed in the third quadrant of the counter-balancer-side weight portion 612B, and a side S26 as the first side is formed in the fourth quadrant. In this example, no second side contiguous with the first side is formed.

[0085] In FIG. 26C, a side S27 is formed in the third quadrant of the counter-balancer-side weight portion 612B, and a side S27 is formed in the fourth quadrant. Therefore, either one of the side S26 and the side S25 corresponds to the first side formed in either one or both of the third quadrant and the fourth quadrant of the coordinate system in the counter-balancer-side weight portion 612B. When the side S27 is defined as the first side, the side S28 corresponds to the side contiguous with the side S27, i.e., the second side. When the side S28 is defined as the first side, the side S27 corresponds to the side contiguous with the side S28, i.e., the second side.

[0086] In FIG. 26D, a side S29, a side S30, and a side S31 are formed in the counter-balancer-side weight portion 612B. Therefore, one of the side S29, the side S30, and the side S31 corresponds to the first side formed in either one or both of the third quadrant and the fourth quadrant of the coordinate system in the counter-balancer-side weight portion 612B. When the side S29 is defined as the first side, the side S30 corresponds to the side contiguous with the side S29, i.e., the second side.

[0087] When the side S30 is defined as the first side, both of the side S29 and the side S31 correspond to the side contiguous with the side S30, i.e., the second side. When the side S31 is defined as the first side, the side S30 corresponds to the side contiguous with the side S31, i.e., the second side. The side S31 is formed in the fourth quadrant of the X-Y coordinate system. The side S30 is formed so as to be continuous in both of the third quadrant and the fourth quadrant of the X-Y coordinate system, and is formed in parallel to the X-axis. The side S29 is formed in the third quadrant of the X-Y coordinate system.

[0088] As described above, with respect to the balancer portion 61B, as long as the areas, in the X-Y coordinate system, of the balancer-side weight portion 612A and the counter-balancer-side weight portion 612B have the relationship of the area of the balancer-side weight portion 612A >the area of the counter-balancer-side weight portion 612B, various examples are conceivable with respect to the formation of the first side formed in the counterbalancer-side weight portion 612B, and the side contiguous with the first side, i.e., the second side.

[0089] Further, the counter-balancer-side weight portion 612B is formed in a polygonal shape including the first side and the second side, and the side and the side are set to be at a right angle or to be parallel to each other. Therefore, the first side and the second side can be simultaneously produced by a single tool, and thus, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll can be highly accurately canceled, and thus, vibration is reduced, and the reliability can be improved.

[0090] Further, processing by a general-purpose machine such as a two-axis lathe can be performed. Since simultaneous processing with another part can be performed, control of the position of the center of gravity is facilitated. Accordingly, the centrifugal force of the orbiting scroll can be highly accurately canceled, and thus, vibration is reduced, and the reliability can be improved. Since processing by a general-purpose machine can be performed, capital investment is reduced, whereby low cost can be realized.

[0091] According to the scroll compressor of embodiment 4 having the configuration as described above, effects similar to those of each embodiment described above are exhibited, the balancer-side weight portion is formed in a mushroom shape that has: a semicircular shape having the origin as a center; and a polygonal shape contiguous with the semicircular shape, and the counter-balancer-side weight portion is formed in an inversed protrusion shape contiguous with the polygonal shape . Therefore, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion can be obtained in a simple and assured manner.

[0092] Further, according to the scroll compressor of embodiment 4, when a maximum distance of the semicircular shape of the balancer-side weight portion is defined as Rlmax, and a maximum distance in the X-axis direction of the counter-balancer-side weight portion is defined as Wl, the balancer-side weight portion and the counter-balancer-side weight portion are formed so as to have a relationship of Rlmax>Wl. Therefore, the relationship of the area of the balancer-side weight portion >the area of the counter-balancer-side weight portion can be obtained in a simpler and further assured manner.

[0093] Embodiment 5 Next, a crankshaft 6 of embodiment 5 will be described with reference to the drawings. FIG. 12A is a side view of the crankshaft according to embodiment 5. FIG. 12B is a top view of the crankshaft according to embodiment 5, viewed from the U-side (arrow Z) direction in FIG. 12A. FIG. 13A shows an enlarged view of the balancer portion 61B in FIG. 12A. FIG. 13B shows a sectional projection view along a line A-A in FIG. 12A. FIG. 14A is a side view of another crankshaft according to embodiment 5. FIG. 14B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 14A. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted.

[0094] As shown in FIG. 13, the balancer-side weight portion 612A is similar to that in FIG. 4 of embodiment 1 described above. The counter-balancer-side weight portion 612B has a planar shape similar to that in FIG. 9B of embodiment 3 described above. In addition, in the counterbalancer-side weight portion 612B, from a position separated by a predetermined distance H4 from the X-axis, to the distance H3, a cut portion 612K as a recessed portion is axially provided over a width WL1 in the rotation axis 6CL direction from the position of a width WL2 from the end surface of the main bearing portion 61A. The distance H4 is a distance of the same dimension as d / 4, but not limited thereto .

[0095] In place of the cut portion 612K, as shown in FIG. 14A and FIG. 14B, a drilled hole 612R as a recessed portion having a predetermined diameter DR may be provided to the counter-balancer-side weight portion 612B. The depth of the drilled hole 612R is set so as to reach the position corresponding to d / 4, but not limited thereto. The scroll compressor 100 including the crankshaft 6 having such a balancer portion 61B has effects similar to those of embodiment 1. Although the drilled hole 612R is adopted in embodiment 5, a blind hole made by an end mill, or the like may be adopted. The shape and the processing method of the hole are not limited thereto.

[0096] According to the scroll compressor of embodiment 5 having the configuration as described above, effects similar to those of each embodiment described above are exhibited, and the counter-balancer-side weight portion has a recessed portion formed therein. Therefore, the weight portion can be reduced in weight.

[0097] According to the scroll compressor of embodiment 5, further, the counter-balancer-side weight portion is provided with the cutout portion that has the predetermined width WL1 in the axial direction of the crankshaft and that extends from the predetermined distance H4 from the X-axis, to the predetermined distance H3. Therefore, a recessed portion can be obtained in a simple manner by means of the cutout portion.

[0098] According to the scroll compressor of embodiment 5, further, on the Y-axis of the portion of the polygonal shape of the counter-balancer-side weight portion, a hole having a predetermined diameter is provided. Therefore, a recessed portion can be obtained in a simple manner by means of the hole.

[0099] Embodiment 6 Next, embodiment 6 will be described. Embodiment 6 is intended to improve the flow of the refrigerant in the middle shell 11 shown in FIG. 2, in order to further improve the efficiency of the scroll compressor 100. When the clearance between the wrap tip of a first wrap 312 of the fixed scroll 31 of the compression drive portion 3 shown in FIG. 2, and the surface on one end side U of a second base plate 321 of the orbiting scroll 32 where a second wrap 322 is provided is defined as Q, a method for adjusting the clearance Q will be described with reference to FIG. 15. FIG. 15 is a partially enlarged sectional view of the compression drive portion 3 in FIG. 2. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted.

[0100] When the dimensions of the respective parts are set as follows, the clearance Q between the wrap tip of the first wrap 312 of the fixed scroll 31 and a surface UA on the one end side of the second base plate 321 of the orbiting scroll 32 can be represented by the following expression.

[0101] L=M+Q+N+T+P and, therefore, Q=L-M-N-T-P Here, L: the distance between a first positioning surface 113 of the middle shell 11 and a second positioning surface 116 of the middle shell 11, M: the distance between the first positioning surface 113 of the middle shell 11 and the wrap tip of the first wrap 312 of the fixed scroll 31, N: the thickness of the second base plate 321 of the orbiting scroll 32, T: the thickness of a thrust plate 24, and P: the distance between the second positioning surface 116 of the middle shell 11 and a flat surface 212 of the first frame 2.

[0102] Here, if the dimensions of the respective parts are known through measurement, it is possible to set a desired clearance Q by adjusting the thickness T of the thrust plate 24 that allows production in various types and amounts. When the clearance Q is adjusted, the refrigerant is suppressed from passing through the clearance Q to leak into the compression space. Thus, loss of the scroll compressor 100 can be reduced.

[0103] According to the scroll compressor of embodiment 6 having the configuration as described above, effects similar to those of each embodiment described above are exhibited, and a thrust plate is provided between a first frame of a compression drive portion and a second base plate of the orbiting scroll. Therefore, leakage of the refrigerant introduced into the scroll compressor can be suppressed. Next, embodiment 7 will be described. FIG. 19A is a side view of a crankshaft according to embodiment 7. FIG. 19B is a sectional projection view along a line A-A of the crankshaft shown in FIG. 19A. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted. As shown in FIG. 19, a mark portion 201 as an individual body identification portion, such as a QR code (registered trademark), for identifying an individual body may be provided to a linear portion 612S of the counterbalancer-side weight portion 612B.

[0105] In a case of a crankshaft in which there is no or substantially no planar portion and in which the curvature of a curved surface portion is small, it has been difficult to provide an individual body identification portion for identifying an individual body. However, in the present disclosure, the linear portion 612S of the counter-balancer-side weight portion 612B is provided. Therefore, when the mark portion 201, such as a QR code (registered trademark), for identifying an individual body is provided, individual bodies can be managed. Thus, high functionality of the compressor that allows reduction in the proportion of defectives, selection of combinations, and the like can be realized.

[0106] In the present embodiment, the mark portion 201 is provided to the linear portion 612S of the counter-balancer-side weight portion 612B, but may be provided to the outer circumferential side of the radius Rlmax of the balancer-side weight portion 612A. When the balancer-side weight portion 612A and the crankshaft 6 are integrally formed in a jointless manner with the same forming material, the balancer-side weight portion 612A has a larger radius than a general crankshaft, and thus, the curvature is reduced, and the individual body identification portion can be provided more easily than in a general case. When the individual body identification portion is provided, individual body management can be performed, and high functionality of the scroll compressor 100 that allows reduction in the proportion of defectives, selection of combinations, and the like can be realized.

[0107] According to the scroll compressor of embodiment 7 having the configuration as described above, effects similar to those of each embodiment described above are exhibited, and the balancer portion is provided with an individual body identification portion. Therefore, individual body management can be performed, and high functionality of the scroll compressor that allows reduction in the proportion of defectives, selection of combinations, and the like can be realized.

[0108] Embodiment 8 Next, embodiment 8 will be described. FIG. 20A is a side view of a crankshaft according to embodiment 8. FIG. 20B is a top view of the crankshaft according to embodiment 8. FIG. 21 is a sectional view of a scroll compressor according to embodiment 8. FIG. 22 is a partial sectional view of the scroll compressor according to embodiment 8. FIG. 23 is a partial sectional view of another scroll compressor according to embodiment 8. In the drawings, parts similar to those in each embodiment described above will be denoted by the same reference characters, and description thereof will be omitted.

[0109] As shown in FIG. 20 to FIG. 22, the balancer cover 301 is fixed, not to the first frame 2, but to the end surface on the U-side of the balancer portion 61B of the crankshaft 6, by means of, for example, a hole 302 for fixation with a bolt or the like, and a bolt 303. The balancer cover 301 is attached, not to the first frame 2, but via the bolt 303 to the hole 302 for fixation provided in the end surface on the U-side of the balancer portion 61B of the crankshaft 6.

[0110] Since the balancer cover 301 is integrated, not with the first frame 2, but with the crankshaft 6, a concern that the balancer portion 61B is deformed due to rotation and comes into contact with the balancer cover 301 is eliminated. Therefore, the diameter of the balancer portion 61B can be increased. Accordingly, a larger centrifugal force of the orbiting scroll 32 can be coped with, the rotational speed of the scroll compressor 100 can be increased or the scrolls can be increased in size, and the compression amount of the scroll compressor 100 can be increased.

[0111] The position where the hole 302 is formed is preferably provided in the vicinity of the outer circumference on the balancer-side weight portion 612A side, as shown in FIG. 20B. When the hole 302 is provided on the balancer-side weight portion 612A side, the centrifugal force of the orbiting scroll can be further canceled by an amount corresponding to the weight of the bolt 303.

[0112] As another example, as shown in FIG. 23, the hole 302 for fixation with a bolt or the like, and the bolt 303 may be provided to an outer circumferential portion of the radius Rlmax of the balancer-side weight portion 612A. Since the position of the bolt 303 is farther with respect to the rotation axis 6CL, the centrifugal force of the orbiting scroll can be further canceled. When the bolt 303 is to fastened to the hole 302, a weight 304 may be installed. When the bolt 303 is to be fastened, an adhesive for loosening prevention is preferably used.

[0113] According to the scroll compressor of embodiment 8 having the configuration as described above, effects similar to those of each embodiment described above are exhibited, and the balancer cover is installed so as to be fixed to the balancer portion. Since the balancer cover and the balancer portion are integrated, a concern that the balancer portion is deformed due to rotation and comes into contact with the balancer cover is eliminated.

[0114] Although the present disclosure is described above in terms of various exemplary embodiments and implementations, it should be understood that the various features, aspects, and functionality described in one or more of the individual embodiments are not limited in their applicability to the particular embodiment with which they are described, but instead can be applied, alone or in various combinations to one or more of the embodiments of the disclosure . It is therefore understood that numerous modifications which have not been exemplified can be devised without departing from the scope of the present disclosure. For example, at least one of the constituent components may be modified, added, or eliminated. At least one of the constituent components mentioned in at least one of the preferred embodiments may be selected and combined with the constituent components mentioned in another preferred embodiment. DESCRIPTION OF THE REFERENCE CHARACTERS

[0115] 1 shell 5 100 scroll compressor 11 middle shell 113 first positioning surface 116 second positioning surface 10 12 upper shell 13 lower shell 15 15 discharge pipe 2 first frame 212 flat surface 22 bearing portion 24 thrust plate 2A bearing portion 3 compression drive portion 20 301 balancer cover 302 hole 303 bolt 25 304 weight 31 fixed scroll 312 first wrap 32 orbiting scroll 321 second base plate 322 second wrap 34 compression chamber 4 drive portion 4A rotor 5 second frame 5A sub bearing portion 6 crankshaft 60 oil passage 61 main shaft portion 611 flange portion 612 weight portion 612A balancer-side weight portion 612B counter-balancer-side weight portion 612BB elliptical shape 612K cut portion 612R drilled hole 612S linear portion 61A main bearing portion 61B balancer portion 61C rotor shrink fit portion 61D sub bearing portion 61G first center of gravity 62 eccentric shaft portion 62C second center of gravity 62CL eccentric axis 65 sleeve bearing 66 balancer 6CL rotation axis Q clearance The following labelled clauses set out further aspects of the present invention: [1] A scroll compressor comprising: a crankshaft supported by a bearing fixed to a shell; a drive portion for the crankshaft; an orbiting scroll provided to an eccentric shaft portion of the crankshaft; and a fixed scroll provided to the shell, wherein a main shaft portion of the crankshaft is provided with a balancer portion that is formed as an integrally-formed object and that decreases a non-equilibrium force associated with rotation of the crankshaft. [2] The scroll compressor according to clause 1, wherein the balancer portion is composed of a balancer-side weight portion and a counter-balancer-side weight portion, and the balancer-side weight portion and the counterbalancer-side weight portion are provided so as to be continuous with a plane including a rotation axis of the crankshaft, and in order to realize a relationship of a weight of the balancer-side weight portion >a weight of the counter-balancer-side weight portion, an area in at least one cross section being a cross section vertical to the rotation axis has a relationship of an area of the balancer-side weight portion >an area of the counter-balancer-side weight portion. [3] The scroll compressor according to clause 2, wherein in a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin, the counter-balancer-side weight portion has a first side in either one or both of a third quadrant and a fourth quadrant of the coordinate system. [4] The scroll compressor according to clause 3, wherein in the coordinate system at the plane vertical to the rotation axis of the crankshaft, the balancer portion has a second side contiguous with the first side. [5] The scroll compressor according to any one of clauses 2 to 4, wherein in a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin, the balancer-side weight portion and the counter-balancer-side weight portion each have a semicircular shape having the origin as a center, and a maximum distance of the semicircular shape from the origin is formed so as to have a relationship of a maximum distance of the balancer-side weight portion >a maximum distance of the counter-balancer-side weight portion. [6] The scroll compressor according to any one of clauses 2 to 5, wherein a part of an outer shape of the counter-balancer-side weight portion is formed in an elliptical shape or a protrusion / recess shape. [7] The scroll compressor according to any one of clauses 2 to 6, wherein in a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin, with reference to the origin as a center, an angle between a line passing through the origin and a first center of gravity of the balancer-side weight portion and a line passing through the origin and a second center of gravity of the counter-balancer-side weight portion is not less than 90 degrees and not greater than 270 degrees. [8] The scroll compressor according to clause 3, 4, or 7, wherein the balancer-side weight portion has a semicircular shape having the origin as a center, and the counter-balancer-side weight portion is formed in a polygonal shape. [9] The scroll compressor according to clause 3, 4, or the balancer-side weight portion is formed in a mushroom shape that has: a semicircular shape having the origin as a center; and a polygonal shape contiguous with the semicircular shape, and the counter-balancer-side weight portion is formed in an inversed protrusion shape contiguous with the polygonal shape .

[10] The scroll compressor according to clause 8 or 9, wherein when a maximum distance of the semicircular shape of the balancer-side weight portion is defined as Rlmax, and a maximum distance in the X-axis direction of the counter-balancer-side weight portion is defined as Wl, the balancer-side weight portion and the counterbalancer-side weight portion are formed so as to have a relationship of Rlmax>Wl.

[11] The scroll compressor according to any one of clauses 2 to 10, wherein the counter-balancer-side weight portion has a recessed portion formed therein.

[12] The scroll compressor according to any one of the balancer portion is provided with a flange portion continuous, in an axial direction, with the balancerside weight portion.

[13] The scroll compressor according to any one of clauses 1 to 12, wherein a thrust plate is provided between a first frame of a compression drive portion and a second base plate of the orbiting scroll.

[14] The scroll compressor according to any one of clauses 1 to 13, wherein the balancer portion is provided with an individual body identification portion.

[15] The scroll compressor according to any one of clauses 1 to 14, wherein a balancer cover is installed so as to be fixed to the balancer portion.

Claims

[1] A scroll compressor comprising:a crankshaft supported by a bearing fixed to a shell;a drive portion for the crankshaft;an orbiting scroll provided to an eccentric shaft portion of the crankshaft; anda fixed scroll provided to the shell, whereina main shaft portion of the crankshaft is provided with a balancer portion that is formed as an integrally-formed object and that decreases a non-equilibrium force associated with rotation of the crankshaft,the balancer portion is composed of a balancer-side weight portion and a counter-balancer-side weight portion, and the balancer-side weight portion and the counterbalancer-side weight portion are provided so as to be continuous with a plane including a rotation axis of the crankshaft,in order to realize a relationship ofa weight of the balancer-side weight portion >a weight of the counter-balancer-side weight portion,an area in at least one cross section being a cross section vertical to the rotation axis has a relationship ofan area of the balancer-side weight portion >an area of the counter-balancer-side weight portion, andthe balancer portion is provided with a flange portion continuous, in an axial direction, with the balancerside weight portion.[2] The scroll compressor according to claim 1, whereina thrust plate is provided between a first frame of a compression drive portion and a second base plate of the orbiting scroll.[3] The scroll compressor according to any one ofclaims 1 to 2, whereinthe balancer portion is provided with an individual body identification portion.[4] The scroll compressor according to any one ofclaims 1 to 3, whereina balancer cover is installed so as to be fixed to the balancer portion.[5] The scroll compressor according to claim 1, whereinin a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axiswhere the X-axis and the Y-axis cross each other is defined as an origin,the counter-balancer-side weight portion has a first side in either one or both of a third quadrant and a fourth quadrant of the coordinate system.[6] The scroll compressor according to claim 5, whereinin the coordinate system at the plane vertical to the rotation axis of the crankshaft,the balancer portion has a second side contiguous with the first side.[7] The scroll compressor according to claim 5 or 6,whereinin a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin,the balancer-side weight portion and the counter-balancer-side weight portion each have a semicircular shape having the origin as a center, anda maximum distance of the semicircular shape fromthe origin is formed so as to have a relationship of a maximum distance of the balancer-side weight portion >a maximum distance of the counter-balancer-side weight portion.[8] The scroll compressor according to any one ofclaims 5 to 7, whereina part of an outer shape of the counter-balancer-side weight portion is formed in an elliptical shape or a protrusion / recess shape.[9] The scroll compressor according to any one ofclaims 5 to 8, whereinin a coordinate system at a plane vertical to the rotation axis of the crankshaft, when a line on a horizontal plane including the rotation axis is defined as an X-axis, a vertical center line of the crankshaft orthogonal to the X-axis is defined as a Y-axis, and a point on the rotation axis where the X-axis and the Y-axis cross each other is defined as an origin,with reference to the origin as a center,an angle between a line passing through the origin and a first center of gravity of the balancer-side weight portion and a line passing through the origin and a second center of gravity of the counter-balancer-side weight portionis not less than 90 degrees and not greater than 270 degrees.[10] The scroll compressor according to claim 9, whereinthe balancer-side weight portion has a semicircular shape having the origin as a center, andthe counter-balancer-side weight portion is formed in a polygonal shape.[11] The scroll compressor according to claim 9, whereinthe balancer-side weight portion is formed in a mushroom shape that has: a semicircular shape having the origin as a center; and a polygonal shape contiguous with the semicircular shape, andthe counter-balancer-side weight portion is formed in an inversed protrusion shape contiguous with the polygonal shape .[12] The scroll compressor according to claim 10 or 11,whereinwhen a maximum distance of the semicircular shape of the balancer-side weight portion is defined as Rlmax, and a maximum distance in the X-axis direction of the counter-balancer-side weight portion is defined as Wl, the balancer-side weight portion and the counter-balancer-side weight portion are formed so as to have arelationship of Rlmax>Wl.[13] The scroll compressor according to any one ofclaims 5 to 12, wherein5 the counter-balancer-side weight portion has arecessed portion formed therein.

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