WO2022071039A1 - スクロール圧縮機 - Google Patents
スクロール圧縮機 Download PDFInfo
- Publication number
- WO2022071039A1 WO2022071039A1 PCT/JP2021/034697 JP2021034697W WO2022071039A1 WO 2022071039 A1 WO2022071039 A1 WO 2022071039A1 JP 2021034697 W JP2021034697 W JP 2021034697W WO 2022071039 A1 WO2022071039 A1 WO 2022071039A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- balancer
- weight portion
- axis
- scroll compressor
- crank shaft
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
Definitions
- This application relates to a scroll compressor.
- the crank shaft of the scroll compressor may be equipped with a balance weight in order to balance the centrifugal force and moment generated around the shaft.
- a balance weight in order to balance the centrifugal force and moment generated around the shaft.
- it has a rotating shaft and an annular outer peripheral surface, is provided with a balance weight that is fixed to the rotating shaft and rotates together with the rotating shaft, and a part of the outer peripheral surface is used for adjusting the angle position of the balance weight with respect to the rotating shaft.
- a technique for suppressing bending of a rotating shaft by a balance weight in a configuration in which a recess is formed is disclosed (see, for example, Patent Document 1).
- Patent Document 1 selects a balance weight corresponding 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 an erroneous balance weight. There is a risk that the angle will shift when installing the balance weight, which requires advanced assembly equipment, jigs, and complicated assembly work, and the balance weight is fitted to the rotating shaft.
- the shrink fitting since the shrink fitting is adopted, there are problems that a high degree of processing is required, a ring portion for shrink fitting needs to be provided, and the balance weight becomes large.
- the present application discloses a technique for solving the above-mentioned problems, and an object thereof is to provide a small scroll compressor that is easy to assemble.
- the scroll compressor disclosed in the present application includes a crank shaft supported by a bearing fixed to a shell, a drive portion of the crank shaft, a swing scroll provided on an eccentric shaft portion of the crank shaft, and the shell.
- the main shaft portion of the crank shaft is provided with a balancer portion formed as an integral body that reduces the non-equilibrium force associated with the rotation of the crank shaft.
- FIG. 3A is a side view of the crank shaft according to the first embodiment
- FIG. 3B is a top view of the crank shaft according to the first embodiment
- 4A is a side view of the crank shaft according to the first embodiment
- FIG. 4B is a sectional projection view of the crank shaft shown in FIG. 4A along the AA line
- 5A is a side view of another crank shaft according to the first embodiment
- FIG. 5B is a sectional projection view of the other crank shaft shown in FIG. 5A along the AA line
- 6A is a side view of the crank shaft according to the second embodiment
- FIG. 6B is a top view of the crank shaft according to the second embodiment.
- 7A is a side view of the crank shaft according to the second embodiment, and FIG. 7B is a sectional projection view of the crank shaft shown in FIG. 7A along the AA line.
- 8A is a side view of the crank shaft according to the third embodiment, and FIG. 8B is a top view of the crank shaft according to the third embodiment.
- 9A is a side view of the crank shaft according to the third embodiment, and FIG. 9B is a sectional projection view of the crank shaft shown in FIG. 9A along the AA line.
- 10A is a side view of the crank shaft according to the fourth embodiment, and FIG. 10B is a top view of the crank shaft according to the fourth embodiment.
- FIG. 11A is a side view of the crank shaft according to the fourth embodiment, and FIG. 11B is a sectional projection view of the crank shaft shown in FIG. 11A along the AA line.
- 12A is a side view of the crank shaft according to the fifth embodiment, and FIG. 12B is a top view of the crank shaft according to the third embodiment.
- 13A is a side view of the crank shaft according to the fifth embodiment, and FIG. 13B is a sectional projection view of the crank shaft shown in FIG. 13A along the AA line.
- 14A is a side view of another crank shaft according to the fifth embodiment, and FIG. 14B is a sectional projection view of the crank shaft shown in FIG. 14A along the AA line.
- FIG. 18A is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 18B is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 18C is an embodiment.
- FIG. 18D is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 18D is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 18D is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment.
- 19A is a side view of the crank shaft according to the seventh embodiment
- FIG. 19B is a sectional projection view of the crank shaft shown in FIG. 19A along the AA line.
- 20A is a side view of the crank shaft according to the eighth embodiment
- FIG. 20B is a top view of the crank shaft according to the eighth embodiment.
- FIG. FIG. 3 is a partial cross-sectional view of the scroll compressor according to the eighth embodiment.
- FIG. 3 is a partial cross-sectional view of another scroll compressor according to the eighth embodiment.
- FIG. 26A is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 26B is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 26C is an embodiment.
- FIG. 26D is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment
- FIG. 26D is a diagram showing another configuration of the balancer portion at the XY coordinates according to the fourth embodiment.
- FIG. 1 is a perspective view of a vertical scroll compressor 100.
- FIG. 2 is a cross-sectional view of the vertical scroll compressor 100, in which the U side shows the upper side and the L side shows the lower side.
- the U side and the L side refer to the U side and the L side in FIG. 2. Further, since the relationship is the same in the following embodiments, the description thereof will be omitted as appropriate.
- the scroll compressor 100 has a middle shell 11, an upper shell 12, a shell 1 including a lower shell 13, a crank shaft 6 supported by a bearing of the middle shell 11, and a crank as main components. It includes a drive unit 4 for rotationally driving the shaft 6, and a compression drive unit 3 provided with a fixed scroll 31 and a swing scroll 32.
- the crank shaft 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.
- the swing scroll 32 provided on the eccentric shaft portion 62 of the crank shaft 6 swings, and the refrigerant is compressed in the compression chamber 34.
- the compressed refrigerant flows to the discharge pipe 15 via the fixed scroll 31.
- a balancer cover 301 is installed in the balancer portion 61B, which will be described later, provided between the first frame 2 arranged on the L side of the swing scroll 32 and the spindle portion 61.
- the balancer cover 301 holds the refrigerating machine oil that has risen in the scroll compressor 100 together with the refrigerant through the oil passage 60 described later, suppresses the refrigerating machine oil from being taken out of the scroll compressor 100, and is a scroll compressor. It has a function of suppressing a decrease in the heat exchange capacity of the heat exchanger connected to the 100.
- the balancer cover 301 is fixed and installed on the first frame 2 with bolts or the like.
- FIGS. 3A and 3B are a side view of the crank shaft according to the first embodiment
- FIG. 3B is a top view of the crank shaft according to the first embodiment as viewed from the U side (arrow Z) of FIG. 3A
- FIG. 4A shows an enlarged view of the balancer portion 61B of FIG. 3A
- FIG. 4B shows a cross-sectional projection view taken along the line AA of FIG. 4A.
- the vertical center line of the crank axis 6 orthogonal to the X axis is defined as the X axis on the horizontal plane including the rotation axis 6CL at the coordinates on the plane perpendicular to the rotation axis 6CL of the crank axis 6.
- the balancer portion 61B has a balancer side weight portion 612A and an anti-balancer side weight portion 612B as a weight portion 612, and is connected to a plane including the rotation shaft 6CL of the crank shaft 6 to connect to the balancer side weight portion 612A and the anti-balancer.
- a side weight portion 612B is provided.
- the balancer side weight portion 612A is formed in the first quadrant and the second quadrant at the XY coordinates defined above, and the anti-balancer side weight portion 612B is formed in the third quadrant and the fourth quadrant.
- the relationship between the X-axis, the Y-axis, the origin C and the crank shaft 6 and the rotary shaft 6CL, the balancer side weight portion 612A, and the anti-balancer side weight portion 612B 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 shown only in FIG. 4B, and the description thereof is omitted in other similar figures.
- the crank shaft 6 includes an oil passage 60, a spindle portion 61, and an eccentric shaft portion 62.
- the spindle portion 61 is the main portion of the crank shaft 6, and the rotary shaft 6CL is arranged so as to coincide 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 crank shaft 6 with the eccentric shaft 62CL eccentric with respect to the rotating shaft 6CL of the spindle portion 61.
- the oil passage 60 is provided so as to penetrate the crank shaft 6 from the L side end to the U side end.
- the oil passage 60 is provided along the rotation shaft 6CL of the crank shaft 6, but the oil passage 60 may be provided below the X axis in FIG. 4B.
- the spindle portion 61 is provided with a main bearing portion 61A, a balancer portion 61B, a rotor shrink fitting portion 61C, and an auxiliary bearing portion 61D in this order from the U side.
- the rotor shrink fitting portion 61C is provided with the rotor 4A of the drive portion 4 shown in FIG.
- 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.
- a sleeve bearing 65 that follows the rotation of the crank shaft 6 is provided between the bearing portion 2A of the first frame 2 and the main bearing portion 61A of the crank shaft 6.
- the weight portion 612 forming the balancer portion 61B includes a smooth semicircular balancer side weight portion 612A having a radius R1max over the first quadrant and the second quadrant of the XY coordinates.
- a smooth semicircular anti-balancer side weight portion 612B having a radius R2max is provided over the quadrant and the fourth quadrant. That is, a balancer side weight portion 612A and an anti-balancer side weight portion 612B are provided connected to the Y axis.
- radius R1max> radius R2max the balancer side weight portion 612A and the anti-balancer side weight portion 612B are distinguished.
- the weight portion 612A on the balancer side and the weight portion 612B on the anti-balancer side are formed due to the magnitude relationship between the weight and the position of the center of gravity.
- the radius R1max is the maximum distance from the origin C of the balancer side weight portion 612A
- the radius R2max is the maximum distance from the origin C of the anti-balancer side weight portion 612B.
- the first center of gravity 61G of the balancer side weight portion 612A and the second center of gravity 62C of the anti-balancer side weight portion 612B are shown.
- the first center of gravity 61G of the balancer side weight portion 612A and the second center of gravity 62C of the anti-balancer side weight portion 612B exist on the Y axis because the weight portion 612 is targeted to the Y axis and has a smooth semicircular shape. Because it has.
- the flange portion 611 provided in the balancer portion 61B will be described later.
- the planar shape and dimensions of the balancer side weight portion 612A and the anti-balancer side weight portion 612B are set according to the physique (capacity, dimensions, rotation speed, etc.) of the scroll compressor 100, and are not necessarily smooth semicircles.
- the circular shape is not adopted. What is important as a balancer is the product of "the distance of the center of gravity of the balancer from the rotation axis 6CL (the distance from the origin C corresponds to the coordinates on the XY axes)" and "the weight of the balancer”. Is big. Increasing the distance makes it possible to reduce the weight, but increases the spatial dimensions.
- the weight ratio of the balancer side weight portion 612A and the anti-balancer side weight portion 612B is, for example, 4 because the relationship is "weight of balancer side weight portion> weight of anti-balancer side weight portion". It is set to 1. That is, the area ratio in at least one cross section that is vertical to the rotating shaft 6CL is, for example, 4: 1. That is, the area in the cross section perpendicular to the rotating shaft 6CL has a relationship of "area of the balancer side weight portion 612A> area of the anti-balancer side weight portion 612B". Thereby, the relationship of "weight of balancer side weight portion 612A> weight of anti-balancer side weight portion 612B" can be easily obtained.
- the radius R1max of the balancer side weight portion 612A and the radius R2max of the anti-balancer side weight portion 612B show a smooth arc shape.
- 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 adopt an arcuate shape having a partially elliptical or uneven shape (described later in the figure). 24 is used to show the example).
- the radius R1max refers to a portion corresponding to the maximum distance of the balancer side weight portion 612A
- the radius R2max refers to a portion corresponding to the maximum distance of the anti-balancer side weight portion 612B.
- the arc shape of the balancer portion 61B adopts an arc shape having a partially elliptical shape or an uneven shape, which is the same in the following embodiments, and thus the description thereof will be omitted as appropriate.
- 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.
- the balancer portion 61B has a semicircular flange portion 611, a semicircular balancer side weight portion 612A having a radius R1max, and a semicircular anti-balancer side having a radius R2max. It is composed of a weight portion 612 having a shape connecting the weight portion 612B.
- the 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. That is, it has a relationship of distance 611Rmin> d / 2.
- the relationship between the distance 611Rmin and the radius R1max of the balancer side weight portion 612A is set to distance 611Rmin ⁇ radius R1max, but is not limited thereto.
- the flange portion 611 has a function of supporting a bearing provided between the crank shaft 6 and the second frame 5 in the axial direction.
- FIG. 5A is a side view of another crank shaft according to the first embodiment
- FIG. 5B is a sectional projection view of the other crank shaft shown in FIG. 5A along the AA line.
- the balancer side weight portion 612A has a semicircular shape having a linear portion LC1 in the vertical direction at a predetermined distance L1 from the Y axis in the first quadrant
- the anti-balancer side weight portion 612B is predetermined in the fourth quadrant from the Y axis. It is a semicircle having a linear portion LC2 in the Y-axis direction at a distance L2.
- the term “predetermined” refers to a “preset value or thing”, and the same applies to the following description, and the description thereof will be omitted as appropriate.
- 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 ⁇ with respect to the origin C.
- the straight line portion LC1 is a side formed parallel to the Y axis.
- the "side” refers to a "linearly formed portion". Since the content is the same in the following embodiments, the description thereof will be omitted as appropriate.
- the straight line portion LC2 formed on the anti-balancer side weight portion 612B corresponds to one of the first sides formed in either or both of the third quadrant and the fourth quadrant of the XY coordinates, and here. It corresponds to the first side formed in the fourth quadrant. Further, the linear portion LC2 is formed parallel to the Y axis.
- the linear portion LC1 is provided in the first quadrant and the linear portion LC2 is provided in the fourth quadrant, even if the balancer portion 61B provided in the second quadrant and the third quadrant is formed, respectively. Often, it may be a combination of these shapes.
- the planar shape of the flange portion 611 is made semicircular in consideration of workability, but the role of the flange portion 611 is to support the sleeve bearing 65, so the shape is not limited to the semicircular shape.
- the angle ⁇ formed by the line passing through the second center of gravity 62C and the origin C of the side weight portion 612B is preferably set to be 180 degrees, at least 90 degrees or more and 270 degrees or less.
- An example of the angle ⁇ is shown in FIG. 5B.
- the first center of gravity 61G and the rotation axis of the balancer side weight portion 612A pass through the first center of gravity 61G of the balancer side weight portion 612A of the balancer portion 61B and are perpendicular to the rotation axis 6CL of the crank shaft 6.
- the XY coordinates are divided into two on the X axis, the side where the first center of gravity 61G is located is the balancer side weight portion 612A, and the other second center of gravity 62C is located. The side becomes the anti-balancer side weight portion 612B.
- the radius R1max of the arc of the balancer side weight portion 612A and the radius R2max of the arc of the anti-balancer side weight portion 612B are assumed to be the maximum distance from the origin C. , The former is set to be larger. Radius R1max> Radius R2max
- a balancer 66 is provided on the L side of the crank shaft 6 shown in FIG. 2 in order to offset the imbalance caused by the swing of the swing scroll 32.
- the crank shaft 6 is made of a forged steel material, a cast product, or an alloy made by sintering metal powder, and is seamlessly and integrally formed of the same forming material, and is provided as an integral body. All parts including the balancer portion 61B are finished to a predetermined shape and dimensions by machining, for example, N / C (Numerical Control) processing.
- the balancer portion 61B may be intentionally subjected to additional processing in order to improve the balance of the scroll compressor 100.
- the balancer portion 61B provided on the crank shaft 6 rotates to cancel the centrifugal force of the swing scroll 32 that swings eccentrically. , Prevents seizure and wear of bearings. Further, since the balancer portion 61B is provided integrally with the crank shaft 6, the ring portion for shrink fitting can be eliminated, so that the weight portion 612 can be miniaturized and the rigidity of the crank shaft 6 is improved.
- a sleeve bearing 65 can be provided between the bearing portion 22 of the first frame 2 and the main bearing portion 61A of the crank shaft 6, further improving reliability.
- the weight and center of gravity can be controlled with high accuracy by machining all parts of the crank shaft 6 including the balancer portion 61B, and the centrifugal force of the swing scroll 32 can be offset with high accuracy, so that vibration is small and reliability is improved. Can be improved.
- each of the balancer side weight portions 612B can be formed symmetrically with respect to the XY coordinates, and the position of the center of gravity can be easily controlled. Therefore, since the centrifugal force of the swing scroll 32 can be canceled out with high accuracy, vibration is small and reliability can be improved.
- the balancer portion 61B, the flange portion 611, the balancer side weight portion 612A, and the anti-balancer side weight portion 612B can be processed at the same time as other parts of the crank shaft 6 by forming a semicircular shape centered on the origin C. Since it can be processed at the same time, it is easy to control the position of the center of gravity. Therefore, since the centrifugal force of the swing scroll 32 can be canceled out with high accuracy, vibration is small and reliability can be improved.
- the distance 611Rmin from the rotating shaft 6CL to the outermost diameter is formed to be larger than d / 2 of the main bearing portion 61A, the diameter of the balancer portion 61B becomes large, the rigidity can be improved, and the reliability can be improved.
- a part of the outer shape of the anti-balancer side weight portion 612B is formed by an elliptical 612BB.
- the side S22 and the side S23 are formed.
- the sides S22 and S23 formed on the anti-balancer side weight portion 612B correspond to one of the first sides formed in either or both of the third quadrant and the fourth quadrant of the XY coordinates, and the sides.
- S22 corresponds to the first side formed in the fourth quadrant
- side S23 corresponds to the first side formed in the third quadrant.
- the sides S22 and S23 are formed parallel to the Y axis.
- the total weight of the balancer portion 61B can be reduced and the weight portion 612 can be miniaturized.
- the angle ⁇ 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.
- the temperature is set to at least 90 degrees or more and 270 degrees or less, the weight of the anti-balancer side weight portion 612B can be reduced, and the weight portion 612 can be miniaturized. Further, since the centrifugal force of the swing scroll 32 can be canceled out with high accuracy, the vibration is small and the reliability can be improved.
- the second center of gravity of the anti-balancer side weight portion 612B must be passed through the first center of gravity 61G of the balancer side weight portion 612A and on the XY coordinates perpendicular to the rotation shaft 6CL of the crank shaft 6.
- 62C existed, the present invention is not limited to this, and when the second center of gravity 62C of the anti-balancer side weight portion 612B does not exist on the XY coordinates, it is along the rotation axis 6CL direction on the XY coordinates.
- the transferred point can be considered as a substitute for the second center of gravity 62C. Since the same applies to the following embodiments, the description thereof will be omitted as appropriate.
- crank shaft supported by a bearing fixed to the shell the driving portion of the crank shaft, the swing scroll provided on the eccentric shaft portion of the crank shaft, and the fixed scroll provided on the shell are provided. Since the main shaft portion of the crank shaft is provided with a balancer portion formed into an integral body that reduces the non-equilibrium force accompanying the rotation of the crank shaft, the balancer portion is provided. Since the non-equilibrium force due to the rotation of the crank shaft can be reduced in the balancer portion, the assembly work is easy and the size can be reduced.
- the balancer portion is composed of a balancer side weight portion and an anti-balancer side weight portion, is connected to a plane including a rotation axis of the crank shaft, and is provided with the balancer side weight portion and the anti-balancer side weight portion.
- the area of at least one cross section that is vertical to the axis of rotation is Since there is a relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side, Only by making the relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side, it is possible to easily obtain a balancer portion capable of reducing the non-equilibrium force accompanying the rotation of the crank shaft.
- 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, By forming the first side, The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be easily obtained.
- the scroll compressor of the first embodiment Since the first side is formed by a side parallel to the Y axis, It can be machined with a general-purpose machine such as a 2-axis lathe. Moreover, since it can be processed at the same time as other parts, it becomes easy to control the position of the center of gravity. Therefore, since the centrifugal force of the swing scroll can be canceled with high accuracy, the vibration is small and the reliability can be improved. In addition, since it can be processed with a general-purpose machine, capital investment is reduced and low cost is possible.
- the balancer-side weight portion has a side parallel to the Y-axis 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 portion has a first side parallel to the Y axis 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 the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be easily and surely obtained.
- the scroll compressor of the first embodiment Since a part of the outer shape of the weight portion on the anti-balancer side is formed in an elliptical shape or an uneven shape, The total weight of the balancer can be reduced and the size can be reduced.
- the scroll compressor of the first embodiment With the origin as the center Since the angle between the line passing through the first center of gravity of the balancer side weight portion and the origin and the line passing through the second center of gravity of the anti-balancer side weight portion and the origin is 90 degrees or more and 270 degrees or less. The weight of the weight portion on the anti-balancer side can be reduced, and the size can be reduced. In addition, since the centrifugal force of the swing scroll can be canceled with high accuracy, vibration is reduced and reliability can be improved.
- the balancer portion is provided with a flange portion connected to the balancer side weight portion in the axial direction, the balancer portion is provided.
- the balancer part can be easily supported to other parts by the flange part.
- the scroll compressor of the first embodiment Since the entire shape of the crank shaft is formed by machining, Since the position of the center of gravity can be easily controlled and the centrifugal force of the swing scroll can be canceled with high accuracy, there is little vibration and reliability can be improved.
- the spindle portion of the crank shaft is provided with a balancer portion formed into an integral body that reduces the non-equilibrium force accompanying the rotation of the crank shaft.
- a balancer portion formed into an integral body that reduces the non-equilibrium force accompanying the rotation of the crank shaft.
- FIG. 6A is a side view of the crank shaft according to the second embodiment
- FIG. 6B is a top view of the crank shaft according to the second embodiment as viewed from the U side (arrow Z) of FIG. 6A
- 7A shows an enlarged view of the balancer portion 61B of FIG. 6A
- FIG. 7B shows a cross-sectional projection drawing of the AA line of FIG. 6A.
- the same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.
- the balancer portion 61B is not provided with the flange portion 611 shown in FIGS. 3A and 3B of the first embodiment described above. That is, the balancer portion 61B is provided with a balancer side weight portion 612A and an anti-balancer side weight portion 612B. Other than this, it is the same as the first embodiment.
- This configuration has the effect of further reducing the size and weight in addition to the first embodiment.
- the bearing portion 2A of the first frame 2 is processed or the bearing is press-fitted to be installed in the main bearing portion 61A as an alternative. Corresponding bearing.
- the shape shown in FIG. 7B since the shape can be formed by forging or casting, 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 line portion LC1 and the straight line portion LC2 can be formed by cutting from the state shown in FIG. 4B.
- FIG. 8A is a side view of the crank shaft according to the third embodiment
- FIG. 8B is a top view of the crank shaft according to the third embodiment as viewed from the U side (arrow Z) of FIG. 8A.
- FIG. 9A shows an enlarged view of the balancer portion 61B of FIG. 8A
- FIG. 9B shows a cross-sectional projection view taken along the line AA of FIG. 9A.
- FIG. 16 the first side formed in either or both of the third quadrant and the fourth quadrant of the XY coordinates will be described.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the planar shape of the anti-balancer side weight portion 612B is a square shape formed by the straight line portion 612S.
- the square of the weight portion 612B on the anti-balancer side has a shape in which the straight line portion 612S connects the straight line portion 612S forming the width W1 at the position of the distance H3 from the X axis. The intersection of the distance H3 and the width W1 intersects the circumference of the radius R2max, but is not limited to this.
- the straight line portion 612S forming 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 shown in the first embodiment.
- the scroll compressor 100 provided with the crank shaft 6 having such a balancer portion 61B has the same effect as that of the first embodiment.
- the first side refers to a side (straight line portion) formed in either or both of the third quadrant and the fourth quadrant of the coordinates in the anti-balancer side weight portion.
- the second side is a coordinate on a plane perpendicular to the rotation axis of the crank shaft, and refers to a side (straight line portion) connected to the first side of the balancer portion 61B. Since the relationship between the first side and the second side is the same in the following embodiments, the description thereof will be omitted as appropriate.
- the straight portion 612S of the anti-balancer side weight portion 612B is designated as a side S11, a side S12, and a side S13, respectively. Therefore, any one of the side S11, the side S12, and the side S13 corresponds to the first side formed in either or both of the third quadrant and the fourth quadrant of the coordinates in the anti-balancer side weight portion 612B. Then, assuming that the side S11 is the first side, the side S12 corresponds to the side connected to the side S11, that is, the second side.
- both the side S12 and the side S13 correspond to the side connected to the side S12, that is, the second side.
- the side S11 is formed in the fourth quadrant of the XY coordinates and is formed parallel to the Y axis.
- the side S12 is formed by connecting to both the third quadrant and the fourth quadrant 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 is formed parallel to the Y axis.
- 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 coordinates. Therefore, the weight of the anti-balancer side weight portion 612B can be reduced without significantly impairing the rigidity of the crank shaft 6, the weight portion 612 can be miniaturized, and a larger centrifugal force can be canceled. .. In addition, since it is a straight line, it has the effect of being easily machined by a cutting tool such as an end mill.
- the sides S11, S12 and S13 can be formed by cutting from the state shown in FIG. 7B of the second embodiment.
- the same effect as that of each of the above-described embodiments can be obtained, and the same effect can be obtained.
- the balancer portion Since the balancer portion has a second side connected to the first side, The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be easily and surely obtained.
- the balancer side weight portion has a semicircular shape centered on the origin and has a semicircular shape. Since the weight portion on the anti-balancer side is formed in a polygonal shape, The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be easily and surely obtained.
- the maximum distance of the semicircle of the weight portion on the balancer side is R1max. Assuming that the maximum distance of the weight portion on the anti-balancer side in the X-axis direction is W1, Since it was formed in the relationship of R1max> W1 The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be obtained more easily and reliably.
- FIG. 10A is a side view of the crank shaft according to the fourth embodiment
- FIG. 10B is a top view of the crank shaft according to the fourth embodiment as viewed from the U side (arrow Z) direction of FIG. 10A
- 11A shows an enlarged view of the balancer portion 61B of FIG. 10A
- FIG. 11B shows a cross-sectional projection view taken along the line AA of FIG. 11A.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the balancer side weight portion 612A and the anti-balancer side weight portion 612B have a substantially inverted convex shape as a whole.
- the balancer side weight portion 612A has an arc having a radius R1max, and has a shape having a substantially mushroom shape having a width W1 parallel to the X axis from the X axis to a position separated by a predetermined distance H1 and has an anti-balancer side weight.
- Section 612B extends the W1 from the X axis to the position of the distance H2, and connects a straight line parallel to the X axis having a width W2 at a position of a predetermined distance H3 from the X axis and a diagonal line connecting the W1 at the position of the distance H2. It has a shape that connects with.
- the straight portion 612S is provided on the anti-balancer side weight portion 612B side.
- FIG. 17 which will be described later, the intersection of the side S18 and the side S17, the intersection of the side S17 and the side S16, the intersection of the side S16 and the side S15, and the intersection of the side S15 and the side S14 are shown in FIG. 11B. It intersects with the circumference of the radius R2max, but is not limited to this.
- the scroll compressor 100 provided with the crank shaft 6 having such a balancer portion 61B has the same effect as that of the first embodiment.
- each side is referred to as a side S14, a side S15, a side S16, a side S17, a side S18, a side V11, and a side V14. Therefore, any one of the side S14, the side S15, the side S16, the side S17, and the side S18 is formed in the third quadrant, the fourth quadrant, or both of the coordinates in the anti-balancer side weight portion 612B.
- the side V11 and the side V14 correspond to the second side connected to the first side.
- the side S16 is the first side
- the side S15 and the side S17 correspond to the side connected to the side S16, that is, the second side.
- the side S14 is the first side
- the side S15 and the side V11 correspond to the side connected to the side S14, that is, the second side.
- the side S18 is the first side
- the side S17 and the side V14 correspond to the side connected to the side S18, that is, the second side.
- the side S15 is the first side
- the side S14 and the side S16 correspond to the side connected to the side S15, that is, the second side.
- the side S17 is the first side
- the side S18 and the side S16 correspond to the side connected to the side S17, that is, the second side.
- the side S14 is formed by connecting to both the first quadrant and the fourth quadrant of the XY coordinates, 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 by connecting to both the third quadrant and the fourth quadrant 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 by connecting to both the second quadrant and the third quadrant of the XY coordinates, and is formed parallel to the Y axis.
- the side V11 is formed in the first quadrant of the XY coordinates and intersects the side S14 at a right angle. However, it is not limited to a right angle.
- the side V14 is formed in the second quadrant of the XY coordinates and intersects the side S18 at a right angle. However, it is not limited to a right angle.
- the anti-balancer side weight portion 612B extends the width W1 from the X axis to the position of the distance H2, and is a straight line parallel to the X axis having the width W2 at the position of the predetermined distance H3 from the X axis and the position of the distance H2.
- the weight of the anti-balancer side weight portion 612B can be reduced, and the weight portion 612 can be miniaturized. Also, larger cancellations are possible.
- the anti-balancer side weight portion 612B has a side S14 (a part) and a side S18 (a part) which are straight line portions 612S having a length of a distance H2 from the X axis in the XY coordinates, and a width W1. It is formed to include (a part of) a side S14 (a part of) and a side S18 (a part of) which is a straight line portion 612S having. Therefore, the weight of the anti-balancer side weight portion 612B can be further reduced without significantly impairing the rigidity of the crank shaft 6, the weight portion 612 can be further miniaturized, and a larger centrifugal force can be canceled. Play. Moreover, since it is a straight line, it can be easily machined by a cutting tool such as an end mill.
- the anti-balancer side weight portion 612B has side S14 (a part) and side S18 (a part) having a distance H2 in the XY coordinates, and sides S15 or sides S17 and X connected to the side S14 or the side S18. It is formed with sides S16 parallel to the axis. Therefore, the weight of the anti-balancer side weight portion 612B can be further reduced without significantly impairing the rigidity of the crank shaft 6, the weight portion 612 can be further miniaturized, and a larger centrifugal force can be canceled. Play.
- the distance H1 and the distance H2 have the same length.
- a general-purpose machine such as a two-axis lathe at the same time as other parts of the crank shaft 6. Since it can be processed at the same time, it is easy to control the position of the center of gravity. Therefore, since the centrifugal force of the swing scroll 32 can be canceled out with high accuracy, vibration is small and reliability can be improved.
- investment is reduced and it can be manufactured at low cost.
- FIGS. 18, 25, and 26 show only the shape of the balancer portion 61B on the plane at the XY coordinates as in each of the above embodiments, and other parts are omitted.
- FIG. 25 is a cross-sectional view showing the configuration of the member before forming the balancer portion 61B at the XY coordinates as in each of the above-described embodiments, and shows only the planar shape.
- the balancer portion 61B as shown in FIGS. 18 and 26 is obtained, in the present application, for example, the balancer portion 61B of the present application is cut from a columnar member formed by forging or casting. To manufacture. Therefore, before cutting, as shown in FIG. 25, the shape is circular 600 in the XY coordinates. Then, a case where cutting is performed from the state of the circular shape 600 to form the balancer portion 61B will be described.
- the anti-balancer side weight portion 612B is formed with a side S19 as a first side connected to the third quadrant and the fourth quadrant.
- the second side connected to the first side is an example in which the second 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 is formed with a side V15 in the first quadrant and a side V16 in the second quadrant.
- the side S20 as the 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, the side V17 corresponds to the second side.
- the side S21 as the first side is continuously formed from the fourth quadrant of the anti-balancer side weight portion 612B to the balancer side weight portion 612A.
- the side S24 as the first side connected to the third quadrant and the fourth quadrant of the anti-balancer side weight portion 612B is formed.
- the second side connected to the first side is an example in which the second side is not formed.
- the side S25 as the first side is formed in the third quadrant of the anti-balancer side weight portion 612B, and the side S26 as the first side is formed in the fourth quadrant.
- the second side connected to the first side is an example in which the second side is not formed.
- the side S27 is formed in the third quadrant and the side S27 is formed in the fourth quadrant of the anti-balancer side weight portion 612B. Therefore, either the side S26 or the side S25 corresponds to the first side formed in either or both of the third quadrant and the fourth quadrant of the coordinates in the anti-balancer side weight portion 612B. Then, assuming that the side S27 is the first side, the side S28 corresponds to the side connected to the side S27, that is, the second side. Further, assuming that the side S28 is the first side, the side S27 corresponds to the side connected to the side S28, that is, the second side.
- sides S29, sides S30, and sides S31 are formed on the anti-balancer side weight portion 612B. Therefore, any one of the side S29, the side S30, and the side S31 corresponds to the first side formed in either or both of the third quadrant and the fourth quadrant of the coordinates in the anti-balancer side weight portion 612B. Then, assuming that the side S29 is the first side, the side S30 corresponds to the side connected to the side S29, that is, the second side.
- both the side S29 and the side S31 correspond to the side connected to the side S30, that is, the second side.
- the side S31 is the first side
- the side S30 corresponds to the side connected to the side S31, that is, the second side.
- the side S31 is formed in the fourth quadrant of the XY coordinates.
- the side S30 is formed by connecting to both the third quadrant and the fourth quadrant 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.
- the balancer portion 61B has an area of the balancer side weight portion 612A and the anti-balancer side weight portion 612B in XY coordinates. If the area of the balancer side weight portion 612A> the area of the anti-balancer side weight portion 612B, the first side formed on the anti-balancer side weight portion 612B and the side connected to the first side, that is, the second side Various examples can be considered for the formation of edges.
- the anti-balancer side weight portion 612B is formed in a polygonal shape including the first side and the second side, and by making the sides perpendicular or parallel to each other, the first side and the second side are simultaneously one. Since it can be manufactured with a tool, it is easy to control the position of the center of gravity. Therefore, since the centrifugal force of the swing scroll can be canceled with high accuracy, the vibration is small and the reliability can be improved.
- the balancer side weight portion is formed in a semicircular shape centered on the origin and a mushroom shape having a polygonal shape continuous in the semicircular shape. Since the anti-balancer side weight portion is formed in a reverse convex shape connected to the polygonal shape, The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be easily and surely obtained.
- the scroll compressor of the fourth embodiment Assuming that the maximum distance of the semicircular shape of the weight portion on the balancer side is R1max and the maximum distance of the weight portion on the anti-balancer side in the X-axis direction is W1. Since it was formed in the relationship of R1max> W1, The relationship of the area of the weight portion on the balancer side> the area of the weight portion on the anti-balancer side can be obtained more easily and reliably.
- FIG. 12A is a side view of the crank shaft according to the fifth embodiment
- FIG. 12B is a top view of the crank shaft according to the fifth embodiment as viewed from the U side (arrow Z) direction of FIG. 12A.
- FIG. 13A shows an enlarged view of the balancer portion 61B of FIG. 12A
- FIG. 13B shows a cross-sectional projection view taken along the line AA of FIG. 12A.
- 14A is a side view of another crank shaft according to the fifth embodiment
- FIG. 14B is a sectional projection view of the crank shaft shown in FIG. 14A along the AA line.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the balancer side weight portion 612A is the same as FIG. 4 of the above-described first embodiment.
- the anti-balancer side weight portion 612B has the same planar shape as that of FIG. 9B of the third embodiment described above, and reaches a distance H3 from a position separated from the X axis by a predetermined distance H4 and has a width from the end face of the main bearing portion 61A in the axial direction.
- a notch portion 612K as a recess is provided over the width WL1 in the rotation axis 6CL direction.
- the distance H4 has the same dimensions as d / 4, but is not limited thereto.
- the anti-balancer side weight portion 612B may be provided with a drill hole 612R as a recess having a predetermined diameter DR instead of the notch portion 612K.
- the depth of the drill hole 612R is set to a position reaching d / 4, but is not limited to this.
- the scroll compressor 100 provided with the crank shaft 6 having such a balancer portion 61B has the same effect as that of the first embodiment.
- the drilled hole 612R is used in the fifth embodiment, the shape and processing method of the hole are not limited to the blind hole by the end mill.
- the same effect as that of each of the above-described embodiments is obtained, and the same effect is obtained. Since the weight portion on the anti-balancer side is formed with a recess, The weight part can be reduced in weight.
- the anti-balancer side weight portion is provided with a notch portion having a predetermined width WL1 in the axial direction of the crank shaft and extending from a predetermined distance H4 to a predetermined distance H3 from the X axis. Therefore, the recess can be easily obtained by the notch.
- Embodiment 6 aims 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.
- FIG. 15 is a partially enlarged cross-sectional view of the compression drive unit 3 of FIG.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the gap Q between the tooth 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 swing scroll 32 is as follows. Can be expressed by the formula of.
- 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 tooth tip 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 swing 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.
- a desired gap Q can be set by adjusting the thickness T of the thrust plate 24, which enables a wide variety of mass production. Then, by adjusting the gap Q, it is possible to prevent the refrigerant from leaking into the compressed space through the gap Q, so that the loss of the scroll compressor 100 can be reduced.
- the same effect as that of each of the above-described embodiments is obtained, and the same effect is obtained. Since the thrust plate is provided between the first frame of the compression drive unit and the second substrate of the swing scroll, Leakage of the refrigerant introduced into the scroll compressor can be suppressed.
- FIG. 19A is a side view of the crank shaft according to the seventh embodiment
- FIG. 19B is a sectional projection view of the crank shaft shown in FIG. 19A along the AA line.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the straight portion 612S of the anti-balancer side weight portion 612B may be provided with a mark portion 201 as an individual discrimination portion for discriminating an individual such as a QR code (registered trademark).
- the mark portion 201 is provided on the straight portion 612S of the anti-balancer side weight portion 612B, but it may be provided on the outer peripheral side of the radius R1max of the balancer side weight portion 612A.
- the balancer side weight portion 612A and the crank shaft 6 seamlessly and integrally with the same forming material, the balancer side weight portion 612A has a larger radius than a general crank shaft, so that the curvature becomes smaller and is general.
- the individual discrimination unit can be easily provided as compared with the case where the individual discrimination unit is provided, individual management can be performed, the defect rate can be reduced, and the scroll compressor 100 can be highly functional such as combination selection.
- the same effect as that of each of the above-described embodiments is obtained, and the same effect is obtained. Since the balancer section is provided with an individual discrimination section, Individual management is possible, the defect rate can be reduced, and the scroll compressor can be highly functional, such as combination selection.
- FIG. 20A is a side view of the crank shaft according to the eighth embodiment
- FIG. 20B is a top view of the crank shaft according to the eighth embodiment
- FIG. 21 is a cross-sectional view of the scroll compressor according to the eighth embodiment
- FIG. 22 is a partial cross-sectional view of the scroll compressor according to the eighth embodiment
- FIG. 23 is a partial cross-sectional view of another scroll compressor according to the eighth embodiment.
- the same parts as those of the above embodiments are designated by the same reference numerals and the description thereof will be omitted.
- the balancer cover 301 is not in the first frame 2, but in the end face on the U side of the balancer portion 61B of the crank shaft 6, with holes 302 for fixing bolts and the like, bolts 303, and the like. It is fixed.
- the balancer cover 301 is attached not to the first frame 2 but to the fixing hole 302 provided on the end surface of the balancer portion 61B of the crank shaft 6 on the U side via the bolt 303.
- the balancer cover 301 is integrated with the crank shaft 6 instead of the first frame 2, the balancer portion 61B is deformed by rotation, and there is no concern that the balancer cover 301 will 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 the centrifugal force of the larger swing scroll 32, increase the rotation speed of the scroll compressor 100, or increase the scroll, and increase the compression amount of the scroll compressor 100.
- the formation position of the hole 302 is preferably provided near the outer periphery on the balancer side weight portion 612A side.
- the centrifugal force of the swing scroll can be canceled by the weight of the bolt 303.
- a hole 302 for fixing a bolt or the like and a bolt 303 are provided on the outer circumference of the balancer side weight portion 612A with a radius R1max. It may be provided in the portion. Since the position of the bolt 303 is farther than the rotation shaft 6CL, the centrifugal force of the swing scroll can be further canceled. Further, when the bolt 303 is fastened to the hole 302, the weight 304 may be installed. When fastening the bolt 303, it is preferable to use an adhesive to prevent loosening.
- the same effect as that of each of the above-described embodiments is obtained, and the same effect is obtained. Since the balancer cover is fixedly installed in the balancer portion, the balancer cover is integrated with the balancer portion, so that the balancer portion is deformed by rotation and there is no concern that the balancer cover comes into contact with the balancer cover.
- 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 fitting part, 61D auxiliary bearing part, 61G first center of gravity, 62 eccentric shaft part , 62C 2nd center of gravity, 62CL eccentric shaft, 65 sleeve bearing, 66 balancer, 6CL rotation shaft, Q gap.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
実施の形態1を図に基づいて説明する。図1は、縦型のスクロール圧縮機100の斜視図である。図2は、縦型のスクロール圧縮機100の断面図であり、U側は上側を、L側は下側を示す。なお、他の図において、U側およびL側と示しているのは、当該図2におけるU側およびL側を指すものである。また、当該関係は以下の実施の形態においても同様であるためその説明は適宜省略する。
半径R1max>半径R2max
シェルに固定された軸受に支持されるクランク軸と、前記クランク軸の駆動部と、前記クランク軸の偏心軸部に設けられた揺動スクロールと、前記シェルに設けられた固定スクロールを備え、前記クランク軸の主軸部には、前記クランク軸の回転に伴う非平衡力を低下させる一体物に形成されたバランサ部が設けられたので、
バランサ部にてクランク軸の回転に伴う非平衡力を低下できるので、組立作業が容易で、かつ小型が可能となる。
前記バランサ部は、バランサ側ウェイト部と反バランサ側ウェイト部によって構成され、前記クランク軸の回転軸を含む平面につながって前記バランサ側ウェイト部と前記反バランサ側ウェイト部が設けられているとともに、
前記バランサ側ウェイト部の重量>前記反バランサ側ウェイト部の重量
の関係となるために、
前記回転軸に鉛直な断面であって少なくとも1つ以上の断面における面積が、
前記バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積
の関係を有するので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係とするのみで、クランク軸の回転に伴う非平衡力を低下できるバランサ部を簡便に得ることができる。
前記クランク軸の前記回転軸に鉛直な面における座標で、前記回転軸を含む水平面上の線をX軸とし、前記X軸と直交する前記クランク軸の縦中心線をY軸とし、前記X軸と前記Y軸とが交わる前記回転軸上の点を原点と定義すると、
前記反バランサ側ウェイト部は、前記座標の第3象限または第4象限のいずれか、または両方に第1辺を有するので、
第1辺を形成することで、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便に得ることができる。
前記第1辺は、前記Y軸に平行な辺にて形成されたので、
2軸旋盤のような汎用機械で加工できる。また、他の箇所と同時に加工できることから重心位置のコントロールが容易となる。従って揺動スクロールの遠心力を高精度に相殺できるため、振動が少なく信頼性を向上できる。また汎用機械で加工できるため、設備投資が少なくなり低コストが可能となる。
前記バランサ側ウェイト部は、前記座標の第1象限または第2象限のいずれかに、前記Y軸から距離L1を有する前記Y軸に平行な辺を有し、
前記反バランサ側ウェイト部の前記第1辺は、前記Y軸から距離L2を有する前記Y軸に平行な第1辺を有しており、
距離L1>距離L2の関係、かつ、平行な前記辺と平行な前記第1辺とは前記Y軸に対して同じ側に形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便にかつ確実に得ることができる。
さらに、2軸旋盤のような汎用機械で加工できる。また、他の箇所と同時に加工できることから重心位置のコントロールが容易となる。従って揺動スクロールの遠心力を高精度に相殺できるため、振動が少なく信頼性を向上できる。また汎用機械で加工できるため、設備投資が少なくなり低コストが可能となる。
前記クランク軸の前記回転軸に鉛直な面における座標で、前記回転軸を含む水平面上の線をX軸とし、前記X軸と直交する前記クランク軸の縦中心線をY軸とし、前記X軸と前記Y軸とが交わる前記回転軸上の点を原点と定義すると、
前記バランサ側ウェイト部および前記反バランサ側ウェイト部は、前記原点を中心とする半円状を有し、前記原点から前記半円状の最大距離が、
前記バランサ側ウェイト部の最大距離>前記反バランサ側ウェイト部の最大距離
の関係にて形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便にかつ確実に得ることができる。
前記反バランサ側ウェイト部の外形の一部分は、楕円状または凹凸状にて形成されたので、
バランサ部の総重量を低減でき、小型化が可能となる。
前記原点を中心として、
前記バランサ側ウェイト部の第1重心と前記原点とを通る線と、前記反バランサ側ウェイト部の第2重心と前記原点とを通る線とのなす角度が90度以上270度以下とするので、
反バランサ側ウェイト部の重量を減らすことができ、小型化できる。また、揺動スクロールの遠心力を高精度に相殺できるため、振動が少なく信頼性を向上できる。
前記バランサ部には、前記バランサ側ウェイト部に軸方向につながる鍔部が設けられているので、
バランサ部を鍔部により、他の箇所に支持しやすくできる。
前記クランク軸の全形状が機械加工によって形成されているので、
重心位置のコントロールが容易で揺動スクロールの遠心力を高精度に相殺できるため、振動が少なく信頼性を向上できる。
クランク軸の主軸部には、前記クランク軸の回転に伴う非平衡力を低下させる一体物に形成されたバランサ部が設けられ、
X-Y座標において、
バランサ側ウェイト部の面積>反バランサ側ウェイト部の面積
の関係を有する点は同様であるため、その説明は適宜省略している。
次に、実施の形態2のクランク軸6を図に基づいて説明する。図6Aは実施の形態2によるクランク軸の側面図、図6Bは図6AのU側(矢印Z)方向から見た実施の形態2によるクランク軸の上面図である。なお、図7Aに図6Aのバランサ部61Bの拡大図を示し、図7Bは図6AのA-A線断面投影図を示す。図において、上記実施の形態1と同様の部分は同一符号を付して説明を省略する。
鍔部を設けていないため、小型化、および、軽量化が可能となる。
次に、実施の形態3のクランク軸6を図に基づいて説明する。図8Aは実施の形態3によるクランク軸の側面図、図8Bは図8AのU側(矢印Z)方向から見た実施の形態3によるクランク軸の上面図である。なお、図9Aに図8Aのバランサ部61Bの拡大図を示し、図9Bは図9AのA-A線断面投影図を示す。また、図16において、X-Y座標の第3象限または第4象限のいずれか、または両方に形成された第1辺について説明する。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。
まず、第1辺とは、反バランサ側ウェイト部において、前記座標の第3象限または第4象限のいずれか、または両方に形成された辺(直線部)を指す。また、第2辺とは、クランク軸の前記回転軸に鉛直な面における座標で、バランサ部61Bの第1辺に連なる辺(直線部)を指す。なお、第1辺と第2辺との関係は以下の実施の形態においても同様であるため、その説明は適宜省略する。
前記クランク軸の前記回転軸に鉛直な面における座標で、
前記バランサ部は、前記第1辺に連なる第2辺を有するので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便にかつ確実に得ることができる。
前記バランサ側ウェイト部は、前記原点を中心とする半円状を有し、
前記反バランサ側ウェイト部は、多角形状にて形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便にかつ確実に得ることができる。
前記バランサ側ウェイト部の前記半円状の最大距離をR1maxとし、
前記反バランサ側ウェイト部の前記X軸方向の最大距離をW1とすると、
R1max>W1の関係にて形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係をさらに簡便にかつ確実に得ることができる。
次に、実施の形態4のクランク軸6を図に基づいて説明する。図10Aは実施の形態4によるクランク軸の側面図、図10Bは図10AのU側(矢印Z)方向から見た実施の形態4によるクランク軸の上面図である。なお、図11Aに図10Aのバランサ部61Bの拡大図を示し、図11Bは図11AのA-A線断面投影図を示す。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。
バランサ側ウェイト部612Aの面積>反バランサ側ウェイト部612Bの面積
の関係を有していれば、反バランサ側ウェイト部612Bに形成される第1辺と、第1辺に連なる辺、すなわち第2辺の形成については様々な例が考えられる。
前記バランサ側ウェイト部は、前記原点を中心とする半円状および前記半円状に連なる多角形状を有するキノコ状にて形成され、
前記反バランサ側ウェイト部は、前記多角形状に連なる逆凸形状にて形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係を簡便にかつ確実に得ることができる。
前記バランサ側ウェイト部の前記半円状の最大距離をR1maxとし、前記反バランサ側ウェイト部の前記X軸方向の最大距離をW1とすると、
R1max>W1の関係にて形成されたので、
バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積の関係をさらに簡便にかつ確実に得ることができる。
次に、実施の形態5のクランク軸6を図に基づいて説明する。図12Aは実施の形態5によるクランク軸の側面図、図12Bは図12AのU側(矢印Z)方向から見た実施の形態5によるクランク軸の上面図である。なお、図13Aに図12Aのバランサ部61Bの拡大図を示し、図13Bは図12AのA-A線断面投影図を示す。図14Aは実施の形態5による他のクランク軸の側面図、図14Bは図14Aに示したクランク軸のA-A線断面投影図である。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。
前記反バランサ側ウェイト部は、凹部が形成されているので、
ウェイト部を軽量化できる。
さらに、前記反バランサ側ウェイト部には、前記クランク軸の軸方向に所定の幅WL1を有し、かつ前記X軸から所定の距離H4から所定の距離H3に至る切り欠き部が設けられているので、切り欠き部により簡便に凹部を得ることができる。
さらに、前記反バランサ側ウェイト部の多角形状の部位の前記Y軸上には、所定の直径の穴が設けられているので、穴により簡便に凹部を得ることができる。
次に、実施の形態6について説明する。この実施の形態6はスクロール圧縮機100の効率をさらに向上させるため、図2に示したミドルシェル11内における冷媒の流れを改善することを目的としている。図2に示した圧縮駆動部3の固定スクロール31の第1渦巻体312の歯先と、第2渦巻体322が設けられた揺動スクロール32の第2基板321の1端側Uの面との間の隙間をQとすると、この隙間Qを調整する方法について、図15を用いて説明する。なお、図15は図2の圧縮駆動部3の部分拡大断面図である。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。
従って、
Q=L-M-N-T-P
ここに、
L:ミドルシェル11の第1位置決め面113とミドルシェル11の第2位置決め面116との間の距離
M:ミドルシェル11の第1位置決め面113と固定スクロール31の第1渦巻体312の歯先との間の距離
N:揺動スクロール32の第2基板321の厚み
T:スラストプレート24の厚み
P:ミドルシェル11の第2位置決め面116と第1フレーム2の平坦面212との間の距離
圧縮駆動部の第1フレームと、揺動スクロールの第2基板との間にスラストプレートが設けられているので、
スクロール圧縮機に導入される冷媒のもれを抑制できる。
次に、実施の形態7について説明する。図19Aは実施の形態7によるクランク軸の側面図、図19Bは図19Aに示したクランク軸のA-A線断面投影図である。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。図19に示すように、反バランサ側ウェイト部612Bの直線部612SにQRコード(登録商標)など個体を判別するための個体判別部としてのマーク部201を設けてもよい。
前記バランサ部には、個体判別部が設けられたので、
個体管理ができ、不良率の低減、組合せ選別などのスクロール圧縮機の高機能化を実現すできる。
次に、実施の形態8について説明する。図20Aは実施の形態8によるクランク軸の側面図、図20Bは実施の形態8によるクランク軸の上面図である。図21は実施の形態8によるスクロール圧縮機の断面図である。図22は実施の形態8によるスクロール圧縮機の部分断面図である。図23は実施の形態8による他のスクロール圧縮機の部分断面図である。図において、上記各実施の形態と同様の部分は同一符号を付して説明を省略する。
前記バランサ部には、バランサカバーが固定されて設置されたので
バランサカバーがバランサ部と一体化されたことにより、バランサ部が回転により変形し、バランサカバーに接触する懸念がなくなる。
従って、例示されていない無数の変形例が、本願に開示される技術の範囲内において想定される。例えば、少なくとも1つの構成要素を変形する場合、追加する場合または省略する場合、さらには、少なくとも1つの構成要素を抽出し、他の実施の形態の構成要素と組み合わせる場合が含まれるものとする。
Claims (15)
- シェルに固定された軸受に支持されるクランク軸と、前記クランク軸の駆動部と、前記クランク軸の偏心軸部に設けられた揺動スクロールと、前記シェルに設けられた固定スクロールを備え、前記クランク軸の主軸部には、前記クランク軸の回転に伴う非平衡力を低下させる一体物に形成されたバランサ部が設けられたスクロール圧縮機。
- 前記バランサ部は、バランサ側ウェイト部と反バランサ側ウェイト部によって構成され、前記クランク軸の回転軸を含む平面につながって前記バランサ側ウェイト部と前記反バランサ側ウェイト部が設けられているとともに、
前記バランサ側ウェイト部の重量>前記反バランサ側ウェイト部の重量
の関係となるために、
前記回転軸に鉛直な断面であって少なくとも1つ以上の断面における面積が、
前記バランサ側ウェイト部の面積>前記反バランサ側ウェイト部の面積
の関係を有する請求項1に記載のスクロール圧縮機。 - 前記クランク軸の前記回転軸に鉛直な面における座標で、前記回転軸を含む水平面上の線をX軸とし、前記X軸と直交する前記クランク軸の縦中心線をY軸とし、前記X軸と前記Y軸とが交わる前記回転軸上の点を原点と定義すると、
前記反バランサ側ウェイト部は、前記座標の第3象限または第4象限のいずれか、または両方に第1辺を有する請求項2に記載のスクロール圧縮機。 - 前記クランク軸の前記回転軸に鉛直な面における座標で、
前記バランサ部は、前記第1辺に連なる第2辺を有する請求項3に記載のスクロール圧縮機。 - 前記クランク軸の前記回転軸に鉛直な面における座標で、前記回転軸を含む水平面上の線をX軸とし、前記X軸と直交する前記クランク軸の縦中心線をY軸とし、前記X軸と前記Y軸とが交わる前記回転軸上の点を原点と定義すると、
前記バランサ側ウェイト部および前記反バランサ側ウェイト部は、前記原点を中心とする半円状を有し、前記原点から前記半円状の最大距離が、
前記バランサ側ウェイト部の最大距離>前記反バランサ側ウェイト部の最大距離
の関係にて形成された請求項2から請求項4のいずれか1項に記載のスクロール圧縮機。 - 前記反バランサ側ウェイト部の外形の一部分は、楕円状または凹凸状にて形成された請求項2から請求項5のいずれか1項に記載のスクロール圧縮機。
- 前記クランク軸の前記回転軸に鉛直な面における座標で、前記回転軸を含む水平面上の線をX軸とし、前記X軸と直交する前記クランク軸の縦中心線をY軸とし、前記X軸と前記Y軸とが交わる前記回転軸上の点を原点と定義すると、
前記原点を中心として、
前記バランサ側ウェイト部の第1重心と前記原点とを通る線と、前記反バランサ側ウェイト部の第2重心と前記原点とを通る線とのなす角度が90度以上270度以下とする請求項2から請求項6のいずれか1項に記載のスクロール圧縮機。 - 前記バランサ側ウェイト部は、前記原点を中心とする半円状を有し、
前記反バランサ側ウェイト部は、多角形状にて形成された請求項3または請求項4または請求項7に記載のスクロール圧縮機。 - 前記バランサ側ウェイト部は、前記原点を中心とする半円状および前記半円状に連なる多角形状を有するキノコ状にて形成され、
前記反バランサ側ウェイト部は、前記多角形状に連なる逆凸形状にて形成された請求項3または請求項4または請求項7に記載のスクロール圧縮機。 - 前記バランサ側ウェイト部の前記半円状の最大距離をR1maxとし、
前記反バランサ側ウェイト部の前記X軸方向の最大距離をW1とすると、
R1max>W1の関係にて形成された請求項8または請求項9に記載のスクロール圧縮機。 - 前記反バランサ側ウェイト部は、凹部が形成されている請求項2から請求項10のいずれか1項に記載のスクロール圧縮機。
- 前記バランサ部には、前記バランサ側ウェイト部に軸方向につながる鍔部が設けられている請求項2から請求項11のいずれか1項に記載のスクロール圧縮機。
- 圧縮駆動部の第1フレームと、揺動スクロールの第2基板との間にスラストプレートが設けられている請求項1から請求項12のいずれか1項に記載のスクロール圧縮機。
- 前記バランサ部には、個体判別部が設けられた請求項1から請求項13のいずれか1項に記載のスクロール圧縮機。
- 前記バランサ部には、バランサカバーが固定されて設置された請求項1から請求項14のいずれか1項に記載のスクロール圧縮機。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB2300713.1A GB2611698A (en) | 2020-10-01 | 2021-09-22 | Scroll compressor |
JP2022553854A JP7442668B2 (ja) | 2020-10-01 | 2021-09-22 | スクロール圧縮機 |
CN202180065735.0A CN116348677A (zh) | 2020-10-01 | 2021-09-22 | 涡旋压缩机 |
DE112021005143.1T DE112021005143T5 (de) | 2020-10-01 | 2021-09-22 | Scrollverdichter |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2020-166732 | 2020-10-01 | ||
JP2020166732 | 2020-10-01 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022071039A1 true WO2022071039A1 (ja) | 2022-04-07 |
Family
ID=80950215
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/034697 WO2022071039A1 (ja) | 2020-10-01 | 2021-09-22 | スクロール圧縮機 |
Country Status (5)
Country | Link |
---|---|
JP (1) | JP7442668B2 (ja) |
CN (1) | CN116348677A (ja) |
DE (1) | DE112021005143T5 (ja) |
GB (1) | GB2611698A (ja) |
WO (1) | WO2022071039A1 (ja) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06147146A (ja) * | 1992-10-29 | 1994-05-27 | Hokuetsu Kogyo Co Ltd | スクロール型流体機械 |
JP2014118954A (ja) * | 2012-12-19 | 2014-06-30 | Mitsubishi Electric Corp | スクロール圧縮機 |
WO2015125304A1 (ja) * | 2014-02-24 | 2015-08-27 | 三菱電機株式会社 | 圧縮機 |
WO2016093361A1 (ja) * | 2014-12-12 | 2016-06-16 | ダイキン工業株式会社 | 圧縮機 |
JP2020105933A (ja) * | 2018-12-26 | 2020-07-09 | 株式会社豊田自動織機 | 電動圧縮機 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000073977A (ja) | 1998-09-03 | 2000-03-07 | Hitachi Ltd | 密閉形電動圧縮機 |
JP2016050551A (ja) | 2014-09-01 | 2016-04-11 | ダイキン工業株式会社 | 圧縮機および圧縮機の組立方法 |
WO2018131088A1 (ja) * | 2017-01-11 | 2018-07-19 | 三菱電機株式会社 | 圧縮機 |
-
2021
- 2021-09-22 GB GB2300713.1A patent/GB2611698A/en active Pending
- 2021-09-22 WO PCT/JP2021/034697 patent/WO2022071039A1/ja active Application Filing
- 2021-09-22 JP JP2022553854A patent/JP7442668B2/ja active Active
- 2021-09-22 CN CN202180065735.0A patent/CN116348677A/zh active Pending
- 2021-09-22 DE DE112021005143.1T patent/DE112021005143T5/de active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06147146A (ja) * | 1992-10-29 | 1994-05-27 | Hokuetsu Kogyo Co Ltd | スクロール型流体機械 |
JP2014118954A (ja) * | 2012-12-19 | 2014-06-30 | Mitsubishi Electric Corp | スクロール圧縮機 |
WO2015125304A1 (ja) * | 2014-02-24 | 2015-08-27 | 三菱電機株式会社 | 圧縮機 |
WO2016093361A1 (ja) * | 2014-12-12 | 2016-06-16 | ダイキン工業株式会社 | 圧縮機 |
JP2020105933A (ja) * | 2018-12-26 | 2020-07-09 | 株式会社豊田自動織機 | 電動圧縮機 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2022071039A1 (ja) | 2022-04-07 |
DE112021005143T5 (de) | 2023-08-10 |
GB202300713D0 (en) | 2023-03-01 |
JP7442668B2 (ja) | 2024-03-04 |
GB2611698A (en) | 2023-04-12 |
CN116348677A (zh) | 2023-06-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR101192640B1 (ko) | 동적 부하 분포를 최적화하고 및 진동을 완화시키기 위한 지지 부재 | |
JPH04358784A (ja) | スクロール圧縮機 | |
US5304045A (en) | Closed type motor-driven compressor, a scroll compressor and a scroll lap machining end mill | |
JP6628957B2 (ja) | スクロール圧縮機 | |
KR20180123433A (ko) | 스크롤 압축기 | |
US6135727A (en) | Detachably affixed counterweight and method of assembly | |
EP1347185A2 (en) | Cylindrical roller bearing | |
JP2016173045A (ja) | ローリングシリンダ式容積型流体機械 | |
WO2022071039A1 (ja) | スクロール圧縮機 | |
WO2021147337A1 (zh) | 一种涡旋压缩机 | |
KR101950241B1 (ko) | 스크롤 압축기 하부 베어링 | |
JP2012057747A (ja) | バランサーシャフト | |
WO2018101316A1 (ja) | スクロール圧縮機とその製造方法 | |
AU2018352907B2 (en) | Rotating shaft of rotary compressor and rotary compressor | |
EP3677765B1 (en) | Engine housing assemblies | |
US10801483B2 (en) | Rolling cylinder displacement compressor | |
JP2004197568A (ja) | スクロール圧縮装置とその製造方法 | |
EP2960513B1 (en) | Hermetic compressor | |
CN207111429U (zh) | 用于压缩机的支撑件和具有其的压缩机 | |
JP2005344600A (ja) | 密閉型圧縮機 | |
CN205001195U (zh) | 一种压缩机 | |
CN205779693U (zh) | 压缩机的泵体及具有其的压缩机 | |
JP4748585B2 (ja) | スクロール圧縮機の製造方法 | |
JP2007198335A (ja) | 電動圧縮機 | |
JP2019218861A (ja) | ローリングシリンダ式容積型圧縮機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 21875341 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2022553854 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 202300713 Country of ref document: GB Kind code of ref document: A Free format text: PCT FILING DATE = 20210922 |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 21875341 Country of ref document: EP Kind code of ref document: A1 |