JP2019065780A - Both-rotation scroll-type fluid machine - Google Patents

Abstract

To provide a both-rotation scroll-type compressor, in which a driving side scroll member and a driven side scroll member can be assembled via plural synchronous driving mechanisms.SOLUTION: The compressor comprises a driving side scroll member 70, a driven side scroll member 90, and a pin ring mechanism 15. The pin ring mechanism 15 transmits a driving force to the driven side scroll member 90 from the driving side scroll member 70, so that the driving side scroll member 70 and the driven side scroll member 90 rotate at the same angular speed in the same direction. A distance ρs between rotation shaft lines that is a driving side rotation shaft line CL1 and a driven side rotation shaft line CL2 and a rotation radius ρp satisfy the relationship of ρs<ρp.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a dual-rotation scroll fluid machine.

  2. Description of the Related Art A twin-rotating scroll compressor has been known conventionally (see Patent Document 1). This includes a drive-side scroll and a driven-side scroll that rotates in synchronization with the drive-side scroll, and the driven shaft that supports the rotation of the driven-side scroll with respect to the drive shaft that rotates the drive-side scroll The drive shaft and the driven shaft are rotated at the same angular velocity in the same direction.

Japanese Patent Application Laid-Open No. 2002-310073

  In Patent Document 1 described above, a pinning mechanism is used as a synchronous drive mechanism for synchronizing and rotating the drive scroll and the driven scroll. The turning radius of the ring of the pin ring mechanism is formed equal to the eccentricity e of the driven scroll with respect to the drive scroll (see [0014] of Patent Document 1).

  However, theoretically, the turning radius of the ring is formed to be equal to the eccentricity e, but in practice there are machining tolerances and assembly errors, so if the turning radius of the ring is smaller than the eccentricity e I can not assemble.

  Specifically, as shown in FIG. 3B, when the distance ρs (the amount of eccentricity e) between the rotation axes of the drive scroll and the rotation center of the driven scroll is equal to the rotation radius pp of the pinning mechanism (ρs = pp) , Can be assembled. However, as shown in FIG. 3C, when the rotational radius pp is smaller than the rotational axis distance ss (ρs> ρp), one of the drive scroll and the follower scroll may be assembled (upward in FIG. 3C). Although the pinning mechanism can be incorporated, the other (lower in FIG. 3C) pinning mechanism protrudes by Δ ′ more than the rotation radius pp, and two pinning mechanisms can not be incorporated simultaneously.

  The present invention has been made in view of such circumstances, and provides a dual-rotation scroll type fluid machine in which a drive side scroll member and a driven side scroll member can be assembled via a plurality of synchronous drive mechanisms. The purpose is

In order to solve the above problems, the dual-rotation scroll type fluid machine of the present invention adopts the following means.
That is, in the dual-rotation scroll type fluid machine according to the present invention, the spiral drive side wall is rotationally driven about the drive side rotation axis by the drive unit and installed with a predetermined angular interval around the center of the drive side end plate. A driven side scroll member having a body and a driven side wall which is rotationally driven about the driven side rotation axis and is installed with a predetermined angle interval around the center of the driven end plate, corresponding to each of the driving side walls A driven-side scroll member which has a body, and each of the driven side-wall members is engaged with the corresponding drive side wall member to form a compression space, the drive-side scroll member and the driven-side scroll member A plurality of synchronous drive mechanisms for transmitting a driving force from the drive-side scroll member to the driven-side scroll member so as to rotate in the same direction at the same angular velocity; The rotational axis distance .rho.s is the distance between the driven side rotational axis to the side the rotational axis, and the rotation radius .rho.p of the synchronous drive mechanism is characterized by satisfying the relation of .rho.s <.rho.p.

The drive side wall disposed at a predetermined angular interval around the center of the end plate of the drive side scroll member is engaged with the driven side wall of the driven side scroll member. The drive-side scroll member is rotationally driven by the drive unit, and the driving force transmitted to the drive-side scroll member is transmitted to the driven-side scroll member via the synchronous drive mechanism. Thus, the driven scroll member rotates and performs rotational motion at the same angular velocity in the same direction with respect to the drive scroll member. Thus, there is provided a dual-rotation scroll-type fluid machine in which both the drive-side scroll member and the driven-side scroll member rotate.
The distance between the rotation axes 軸 s and the rotation radius pp of the synchronous drive mechanism are made to satisfy the relationship ρs <ρp. Thereby, the drive side scroll member and the driven side scroll member can be assembled via the plurality of synchronous drive mechanisms. Even if processing tolerances or assembly errors occur, assembly is possible because the scroll members rotate relatively slightly.
As a synchronous drive mechanism, a pin ring mechanism is mentioned, for example.

  Further, in the dual rotation scroll type fluid machine of the present invention, the theoretical theoretical radius thth of the mesh between the drive side wall and the driven side wall and the distance between the rotation axes ss satisfy the relation ρth >> s. .

If the distance 回 転 s between the rotation axes is larger than the theoretical theoretical radius 合 う th where the drive side wall and the driven side wall mesh with each other, the drive side wall and the driven side wall interfere with each other, making it impossible to assemble. In addition, even when the theoretical scroll radius thth and the distance ss between the rotation axes are equal, there are cases where assembly can not be performed due to processing tolerances or assembly errors. Therefore, the drive side scroll member and the driven side scroll member can be assembled by making the theoretical scroll radius thth larger than the rotational axis distance ss.
The theoretical scroll radius means a turning radius when each scroll member relatively pivots when the driving side wall body and the driven side wall body mesh without gap in drawing.

  Furthermore, in the dual-rotating scroll fluid machine of the present invention, the minimum gap Δmin between the drive side wall and the driven side wall is obtained when the drive side scroll member and the driven side scroll member are relatively twisted. The turning radius pp is set to be larger than 0.

  When ρs <ρp, a gap is generated between the drive side wall and the driven side wall, and the drive side scroll member and the driven side scroll member are relatively twisted during operation, and the drive side wall and the driven side wall The clearance Δ between the body and the body may be reduced, and the walls may be in contact with each other. Therefore, the rotation radius pp is set so that the minimum gap Δmin between the wall bodies is larger than zero. Thus, excessive contact between the walls can be avoided to prevent noise reduction and failure.

  Further, in the dual rotation scroll type fluid machine of the present invention, the drive side wall body and the driven side wall body are respectively formed by an involute curve having a base circle radius b, and the drive side rotation axis and the driven side rotation axis When the distance between the middle point of and the center of the rotation radius pp is Rsp, ρp <ρs + Rsp × (ρth−ρs) / b is satisfied.

  When the drive side wall and the driven side wall are created by the involute curve, ρ p is set so as to satisfy the above equation. Thus, the rotation radius 半径 p is set such that the minimum gap Δmin between the wall bodies is larger than 0, and excessive contact between the wall bodies can be avoided to prevent noise reduction and failure.

  In the dual-rotating scroll type fluid machine of the present invention, a spiral drive side wall body is rotationally driven by the drive unit about the drive side rotation axis and installed with a predetermined angular interval around the center of the drive side end plate And a spiral driven side wall member which is rotationally driven about the driven side rotation axis and has a predetermined angular interval around the center of the driven side plate, and corresponds to each of the driving side wall members. A driven side scroll member which forms a compression space by meshing each of the driven side walls with the corresponding drive side wall, and the drive side scroll member and the driven side scroll member are the same. A plurality of synchronous drive mechanisms for transmitting a driving force from the drive-side scroll member to the driven-side scroll member so as to rotate in the same angular velocity in the same direction; A crankpin having a first eccentric shaft portion and a second eccentric shaft portion having eccentric axes eccentric to each other, and provided between an end portion of each of the eccentric shaft portions and the drive side scroll member and the driven side scroll member A crank mechanism comprising a first crank pin end rolling bearing and a second crank pin end rolling bearing, and a distance 回 転 s between rotation axes which is a distance between the drive side rotation axis and the driven side rotation axis; The rotation radius pp of the synchronous drive mechanism satisfies the relationship ss = pp, and a gap is provided at a position where the first crank pin end rolling bearing and / or the second crank pin end rolling bearing is fitted. It is characterized by

The drive side wall disposed at a predetermined angular interval around the center of the end plate of the drive side scroll member is engaged with the driven side wall of the driven side scroll member. The drive-side scroll member is rotationally driven by the drive unit, and the driving force transmitted to the drive-side scroll member is transmitted to the driven-side scroll member via the synchronous drive mechanism. Thus, the driven scroll member rotates and performs rotational motion at the same angular velocity in the same direction with respect to the drive scroll member. Thus, there is provided a dual-rotation scroll-type fluid machine in which both the drive-side scroll member and the driven-side scroll member rotate.
If the synchronous drive mechanism is a crank mechanism provided with a crank pin, since the bearing supports the end of the crank pin, twisting of each scroll member can not be permitted as in the pin ring mechanism.
Therefore, the rotational axis distance 軸 s and the rotational radius 半径 p of the synchronous drive mechanism satisfy the relationship 軸 s = ρp, and the first crankpin end rolling bearing and / or the second crankpin end rolling bearing is A gap is provided at the position to be fitted. Thus, the drive-side scroll member and the driven-side scroll member can be assembled via the synchronous drive mechanism. Even if processing tolerances or assembly errors occur, assembly is possible because the scroll members rotate relatively slightly.

  Further, in the dual rotation scroll type fluid machine of the present invention, an elastic member is disposed in the gap.

  By arranging the elastic member in the gap, the reliability can be improved by reducing the vibration of the synchronous drive mechanism when a load is applied.

  Since the rotation axis distance 間 s, which is the distance between the drive side rotation axis and the driven side rotation axis, is smaller than the rotation radius pp of the synchronous drive mechanism, the drive side scroll member and the driven side scroll via the plurality of synchronous drive mechanisms The parts can be assembled.

BRIEF DESCRIPTION OF THE DRAWINGS It is the longitudinal cross-sectional view which showed the twin-rotating scroll type compressor concerning 1st Embodiment of this invention. It is the longitudinal cross-sectional view which showed the pin ring mechanism. It is the model which showed the relationship between the rotation radius (rho) p of 1st Embodiment, and the distance 回 転 s between rotation axes. It is the schematic diagram which showed the relationship between the rotation radius (rho) p as a comparative example, and the distance 軸 s between rotation axes. It is the schematic diagram which showed the relationship between the rotation radius (rho) p as a comparative example, and the distance 軸 s between rotation axes. It is the top view which showed the wall of scroll member. It is the enlarged view which showed area | region AR1 of FIG. It is the enlarged view which showed area | region AR2 of FIG. It is the graph which showed the fluctuation of the crevice of Drawing 5A. It is the graph which showed the fluctuation of the crevice of Drawing 5B. FIG. 6 is a schematic view showing a relationship between a theoretical scroll radius thth and a distance between rotational axes 回 転 s. FIG. 6 is a schematic view showing a geometrical relationship between a rotation radius pp and a distance 回 転 s between rotation axes. It is a schematic diagram showing a pin ring mechanism. It is the model which showed the pin ring mechanism concerning 2nd Embodiment of this invention. It is a schematic diagram showing the modification of a 2nd embodiment. It is the model which showed the other modification of 2nd Embodiment.

First Embodiment
Hereinafter, a first embodiment of the present invention will be described with reference to FIG.
FIG. 1 shows a dual-rotation scroll compressor (double-rotation scroll fluid machine) 1. The double-rotating scroll compressor 1 can be used, for example, as a turbocharger that compresses combustion air (fluid) supplied to an internal combustion engine such as a vehicle engine.

  The double-rotating scroll compressor 1 includes a housing 3, a motor (drive unit) 5 housed on one end side of the housing 3, and a drive-side scroll member 70 and a driven-side scroll member housed on the other end side of the housing 3. It has 90 and.

The housing 3 has a substantially cylindrical shape, and includes a motor accommodating portion 3 a that accommodates the motor 5 and a scroll accommodating portion 3 b that accommodates the scroll members 70 and 90.
Cooling fins 3c for cooling the motor 5 are provided on the outer periphery of the motor housing 3a. At the end of the scroll housing portion 3b, a discharge port 3d for discharging the compressed air is formed. Although not shown in FIG. 1, the housing 3 is provided with an air inlet for drawing air.

  The scroll housing portion 3 b of the housing 3 is divided at a division plane P located substantially at the center of the scroll members 70 and 90 in the axial direction. The housing 3 is provided with a flange portion (not shown) that protrudes outward at a predetermined position in the circumferential direction. The division surface P is fastened by fixing to this flange portion through a bolt or the like as a fastening means.

  The motor 5 is driven by supplying power from a power supply source (not shown). The rotation control of the motor 5 is performed by a command from a control unit (not shown). The stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3. The rotor 5b of the motor 5 rotates around the drive side rotation axis CL1. The drive shaft 6 extending on the drive side rotation axis line CL1 is connected to the rotor 5b. The drive shaft 6 is connected to the drive side shaft portion 7 c of the drive side scroll member 70.

The drive side scroll member 70 includes a first drive side scroll portion 71 on the motor 5 side and a second drive side scroll portion 72 on the discharge port 3 d side.
The first drive side scroll portion 71 includes a first drive side end plate 71a and a first drive side wall 71b.
The first drive side end plate 71a is connected to the drive side shaft 7c connected to the drive shaft 6, and extends in a direction orthogonal to the drive side rotation axis CL1. The drive side shaft portion 7 c is rotatably provided with respect to the housing 3 via a drive side bearing 11 formed as a ball bearing.

  The first drive side end plate 71a has a substantially disc shape in a plan view. A spiral first drive side wall 71b is provided on the first drive side end plate 71a.

The second drive side scroll portion 72 includes a second drive side end plate 72a and a second drive side wall 72b. The second drive side wall 72b is spiral like the first drive side wall 71b described above.
A second drive side shaft portion 72c extending in the direction of the drive side rotation axis CL1 is connected to the second drive side end plate 72a. The second drive side shaft portion 72c is rotatably provided relative to the housing 3 via a second drive side bearing 14 which is a ball bearing. The second drive side shaft portion 72c is formed with a discharge port 72d along the drive side rotational axis CL1.

  The first drive side scroll portion 71 and the second drive side scroll portion 72 are fixed in a state in which the tips (free ends) of the wall bodies 71 b and 72 b face each other. Fixing of the first drive side scroll portion 71 and the second drive side scroll portion 72 is performed by bolts 31 fastened to flange portions 73 provided at a plurality of places in the circumferential direction so as to protrude radially outward. .

  The driven scroll member 90 includes a first driven scroll portion 91 and a second driven scroll portion 92. The driven side end plates 91a and 92a are located substantially at the center of the driven side scroll member 90 in the axial direction (horizontal direction in the drawing). The two driven end plates 91a and 92a are fixed in a state where their respective back surfaces (other side surfaces) are overlapped and in contact with each other. This fixing is performed by bolts, pins, etc., though not shown. A through hole 90h is formed at the center of each of the driven end plates 91a and 92a, and compressed air flows to the discharge port 72d.

  A first driven side wall body 91b is provided on one side surface of the first driven side end plate 91a, and a second driven side wall body 92b is provided on one side surface of the second driven side end plate 92a. The first driven side wall 91b disposed on the motor 5 side from the first driven side end plate 91a is engaged with the first drive side wall 71b of the first drive side scroll portion 71, and is discharged from the second driven side end plate 92a. The second driven side wall 92 b disposed on the outlet 3 d side is engaged with the second driving side wall 72 b of the second driving scroll portion 72.

  A first support member 33 and a second support member 35 are provided at both ends of the driven scroll member 90 in the axial direction (horizontal direction in the drawing). The first support member 33 is disposed on the motor 5 side, and the second support member 35 is disposed on the discharge port 3 d side. The first support member 33 is fixed to the end (free end) of the first driven side wall 91b by the press-fit pin 25a, and the second support member 35 is the end (free end) of the second driven side wall 92b. Are fixed by press-fit pins 25b. A shaft portion 33 a is provided on the central axis side of the first support member 33, and the shaft portion 33 a is fixed to the housing 3 via a first support member bearing 37. A shaft portion 35 a is provided on the central axis side of the second support member 35, and the shaft portion 35 a is fixed to the housing 3 via a second support member bearing 38. Thus, the driven scroll member 90 is configured to rotate around the driven rotation axis CL2 via the support members 33 and 35.

  The drive side scroll member 70 and the driven side scroll member 90 are arranged offset by a predetermined distance. That is, it is offset by an inter-rotation-axis distance ρs, which is the distance between the drive-side rotation axis CL1 and the driven-side rotation axis CL2.

  A pin ring mechanism (synchronous drive mechanism) 15 is provided between the first support member 33 and the first drive side end plate 71a. The pin ring mechanism 15 includes a pin member 15 b whose one end is inserted in a circular hole 15 a formed in the first support member 33. The other end of the pin member 15b is fixed to the first drive side end plate 71a by press fitting or the like. While the driving force is transmitted from the drive side scroll member 70 to the driven side scroll member 90 by the pin ring mechanism 15, both scroll members 70, 90 rotate at the same angular velocity in the same direction. A plurality of pin ring mechanisms 15 are provided, for example, three at equal angular intervals.

  The pin ring mechanism 15 is shown enlarged in FIG. In the figure, the first drive end plate 71a is shown at the upper side, and the first support member 33 is shown at the lower side. Further, in the circular hole 15a formed in the first support member 33, a rolling bearing 15d such as a ball bearing is provided. The pin ring mechanism 15 may have a configuration in which the rolling bearing 15d is provided as shown in the same drawing, or a configuration in which the rolling bearing is not provided as shown in FIG.

  The pin member 15b is displaced while in contact with the inner circumferential surface of the rolling bearing 15d. Therefore, the turning radius of the pin ring mechanism 15 is a distance from the center of the circular hole 15c to the center of the pin member 15b in contact with the inner ring of the rolling bearing 15d, hereinafter referred to as a turning radius 半径 p.

  Since the inner diameter side of the rolling bearing 15d is a space, the pin member 15b is allowed to move to the inner diameter side of the rolling bearing 15d (moving in the direction of arrow A1 in the figure). As a result, the drive side scroll member 70 and the driven side scroll member 90 relatively twist, and the facing walls approach and separate from each other.

The twin-rotating scroll compressor 1 configured as described above operates as follows.
When the drive shaft 6 is rotated about the drive rotation axis CL1 by the motor 5, the drive shaft 7c connected to the drive shaft 6 is also rotated, whereby the drive scroll member 70 is rotated about the drive rotation axis CL1. Rotate. When the drive side scroll member 70 rotates, the drive force is transmitted from the support members 33 and 35 to the driven side scroll member 90 through the pin ring mechanism 15, and the driven side scroll member 90 rotates around the driven side rotation axis CL2. Do. At this time, when the pin member 15b of the pin ring mechanism 15 moves in contact with the inner circumferential surface of the circular hole, both scroll members 70, 90 rotate at the same angular velocity in the same direction.

  When both scroll members 70, 90 rotate, the air sucked from the suction port of housing 3 is drawn from the outer peripheral side of both scroll members 70, 90, and the compression chamber formed by both scroll members 70, 90 It is taken into the (closed space). The compression chamber formed by the first drive side wall 71b and the first driven side wall 91b and the compression chamber formed by the second drive side wall 72b and the second driven side wall 92b are separately compressed. Ru. The volume of each compression chamber decreases as it moves toward the center, and the air is compressed accordingly. The air compressed by the first drive side wall 71b and the first driven side wall 91b passes through the through holes 90h formed in the driven side end plates 91a and 92a, and the second drive side wall 72b and the second driven side wall The air that has been compressed by the air flow 92b merges, and the air after the merging flows through the discharge port 72d and is discharged from the discharge port 3d of the housing 3 to the outside. The discharged compressed air is led to an internal combustion engine (not shown) and used as combustion air.

[Relationship between turning radius pp and distance between rotation axes ρs]
The relationship between the rotation radius pp (see FIG. 2) and the distance between the rotation axes 軸 s (see FIG. 1) will be described.
As shown in FIG. 3A, the rotation radius pp is set larger than the distance ρs between the rotation axes (ρs <ρp). By setting the dimensional relationship in this manner, one pin ring mechanism 15 can be incorporated and then the other pin ring mechanism 15 can be incorporated.
FIG. 3B shows a case where ss = ρp as a comparative example, and theoretically corresponds to both pinning mechanisms 15. However, if there are processing tolerances and assembly errors, as shown in FIG. 3C, ρs> ρp, and it is impossible to incorporate both pin ring mechanisms 15 simultaneously. Therefore, in the present embodiment, as shown in FIG. 3A, the dimensional relationship is set to satisfy the following expression (1).
ρ s <・ ・ ・ p (1)

Next, setting of the upper limit of pp when ρs <ρp will be described.
The drive side wall 71 b and the driven side wall 91 b are shown in FIG. 4. The contours of the wall bodies 71b and 91b are involute curves created from base circles C1 and C2 having a base circle radius b, respectively.

  FIG. 5A shows an enlarged view of the area AR1 of FIG. The area AR1 is an area in which the back side (outer periphery side) of the driven side wall body 91b is in proximity to the belly side (inner peripheral side) of the drive side wall body 71b. As shown in the center of FIG. 5A, when the drive side scroll member 70 and the driven side scroll member 90 are in the neutral position without causing relative twist, the drive side wall 71b has an initial clearance Δ. And a driven side wall 91b. From this state, when the driven scroll member 90 twists in the right direction (clockwise) with respect to the drive scroll member 70, the gap δ decreases (the state on the right in FIG. 5A) and twists in the left direction (counterclockwise). Then, the gap δ becomes larger (the state on the left side of FIG. 5A). Such fluctuation of the gap δ can be adjusted by the size of the rotation radius pp, and the twist becomes larger if the rotation radius pp is increased.

FIG. 6A shows the change of the gap δ due to the twist shown in FIG. 5A. In the figure, the horizontal axis indicates the size of twist of the scroll members 70 and 90. The vertical axis represents the gap δ between the walls 71 b and 91 b.
As can be seen from FIG. 6A, when the relative twisting of the scroll members 70 and 90 increases in the right direction, the gap δ becomes zero, and the wall bodies 71b and 91b come in contact with each other. In order to avoid this, the radius ρp of rotation is limited to a predetermined value, and the minimum gap Δmin is made larger than zero.

  FIG. 5B shows an enlarged view of the area AR2 of FIG. The area AR2 is an area in which the belly side (inner peripheral side) of the driven side wall body 91b is in proximity to the back side (outer peripheral side) of the drive side wall body 71b. As shown in the center of FIG. 5B, when the drive side scroll member 70 and the driven side scroll member 90 are in the neutral position without causing relative twisting, the drive side wall 71b has an initial gap Δ. And a driven side wall 91b. From this state, when the driven scroll member 90 twists in the right direction (clockwise) with respect to the drive scroll member 70, the gap δ increases (the state on the right in FIG. 5B) and twists in the left direction (counterclockwise). Becomes smaller (the state on the left side of FIG. 5B). Such fluctuation of the gap δ can be adjusted by the size of the rotation radius pp, and the twist becomes larger if the rotation radius pp is increased.

FIG. 6B is a graph similar to FIG. 6A corresponding to FIG. 5B.
As can be seen from FIG. 6B, when the relative twisting of the scroll members 70 and 90 increases in the left direction, the gap δ becomes zero and the wall bodies 71b and 91b come in contact with each other. In order to avoid this, the radius ρp of rotation is limited to a predetermined value, and the minimum gap Δmin is made larger than zero.

[Relationship between scroll theory radius thth and rotation axis distance ρs]
The relationship between the theoretical theoretical radius thth of engagement between the drive side wall 71b and the driven side wall 91b and the distance ss between the rotation axes will be described with reference to FIG.
The theoretical theoretical radius thth of the scroll means a turning radius in the case where the scroll members 70 and 90 relatively turn when the drive side wall 71b and the driven side wall 91b mesh with no gap on the drawing.
As shown in FIG. 7, when the distance 回 転 s between the rotation axes is larger than the theoretical scroll radius thth, the drive side wall 71b and the driven side wall 91b interfere with each other, making it impossible to assemble. In addition, even when the theoretical scroll radius thth and the distance ss between the rotation axes are equal, there are cases where assembly can not be performed due to processing tolerances or assembly errors. Therefore, in the present embodiment, the theoretical scroll radius thth is larger than the distance 軸 s between the rotation axes. That is, the following equation (2) is satisfied.
ρ th> s s (2)

[Upper limit of turning radius pp]
Next, a specific concept of setting the minimum gap Δmin so that the above-mentioned gap δ does not become 0, that is, a method of setting the upper limit value of the rotation radius pp will be described.
FIG. 8 shows the geometrical relationship between the radius 回 転 p of rotation and the distance ρs between the rotation axes. As shown in the figure, the distance between the center of the radius ρp of rotation and the center of the distance ρs between the rotation axes (that is, the midpoint between the drive side rotation axis CL1 and the driven side rotation axis CL2) is Rsp. Then, the twist angle α is expressed by the following equation.
α = (ρp−ρs) / Rsp [rad] (3)
The gap δ is expressed by the following equation using the base circle radius b.
δ = b × α = b × (ρp−ρs) / Rsp (4)
In order to define the theoretical scroll radius thth and the distance between the rotational axes ss so as to allow the gap δ obtained by the above equation (4), the following equation is obtained from the above equation (2).
thth-ρs> δ = b × (ρp-ρs) / Rsp (5)
The following equation is obtained by modifying the above equation (5).
Rsp × (ρth−ρs) / b + ρs> ρp (6)
From the above equation (6), the following relationship is obtained.
ss <ρp <ρs + Rsp × (ρth-ρs) / b (7)
As can be seen from the second term on the right side of the above equation (7), the upper limit value of the rotation radius と な る p is Rsp × (ρth−ρs) / b. If the rotation radius pp is set so as not to exceed the upper limit value, the wall bodies 71b and 91b can be prevented from contacting with each other.

According to the present embodiment, the following effects are achieved.
The distance between the rotation axes ρs and the radius 回 転 p of rotation are made to satisfy the relationship ρs <ρp. Thereby, the drive side scroll member 70 and the driven side scroll member 90 can be assembled via the multiple pin ring mechanism 15. Even if processing tolerances or assembly errors occur, the scroll members 70, 90 may be slightly twisted to enable assembly.

  The drive-side scroll member 70 and the driven-side scroll member 90 can be assembled by making the theoretical scroll radius 大 き く th larger than the rotational axis distance 間 s.

  The rotation radius pp was set such that the minimum gap Δmin between the wall bodies 71b and 91b was larger than zero. Thereby, excessive contact between the wall bodies 71b and 91b can be avoided to prevent noise reduction and failure.

  For the drive side wall 71 b and the driven side wall 91 b created by the involute curve, ρ p is set so as to satisfy the above equation (7). Thus, the rotation radius 半径 p is set such that the minimum gap Δmin between the wall bodies is larger than 0, and excessive contact between the wall bodies can be avoided to prevent noise reduction and failure.

Second Embodiment
Next, a second embodiment of the present invention will be described. The present embodiment is different in that a crank pin mechanism 16 is adopted to the pin ring mechanism 15 used in the first embodiment, and the other points are the same. Therefore, hereinafter, only differences from the first embodiment will be described.

  As shown in FIG. 9, the crankpin mechanism 16 includes a crankpin 16a having a first eccentric shaft portion 16a1 and an second eccentric shaft portion 16a2 having eccentric axes eccentric to each other. The first eccentric shaft 16a1 is provided with a first crank pin end rolling bearing 17a, and the second eccentric shaft 16a2 is provided with a second crank pin end rolling bearing 17b. The first crank pin end rolling bearing 17a is attached to the first drive side end plate 71a (see FIG. 1), and the second crank pin end rolling bearing 17b is attached to the first support member 33 (see FIG. 1) Be

  As described above, since the crank pin mechanism 16 restricts the displacement only in the rotational direction of the bearing by the rolling bearings 17a and 17b, the radial direction (arrow A1 in FIG. 2) as in the pin ring mechanism 15 of the first embodiment. Refer not to allow displacement). Therefore, assembly of scroll members 70 and 90 via crank pin mechanism 16 is enabled by adopting the following concept.

The radius 回 転 p of rotation and the distance ss between the rotation axes should satisfy the following equation.
ρ s = ・ ・ ・ p (8)

Then, as shown in FIG. 10, a gap t1 is formed between the inner ring of the first crank pin end rolling bearing 17a and the first eccentric shaft 16a1. The clearance t1 is set to a size that allows machining intersection and assembly error of the crank pin mechanism 16.
A gap may be provided on the outer ring side of the first crank pin end rolling bearing 17a, or may be provided on the inner ring side or the outer ring side of the second crank pin end rolling bearing 17b.

According to the present embodiment, the following effects are achieved.
A gap is provided at a position where the first crank pin end rolling bearing 17a and / or the second crank pin end rolling bearing 17b is fitted. As a result, the drive side scroll member 70 and the driven side scroll member 90 can be assembled via the crank pin mechanism 16.

In the present embodiment, although the clearances are provided in the crankpin rolling bearings 17a and 17b, the clearances may be provided in the bearings that define the distance 回 転 s between the rotation axes.
Specifically, as shown in FIG. 11, a clearance t2 may be provided on the inner ring side of the bearings 11, 14 (see FIG. 1) supported rotatably around the drive side rotation axis CL1.
A gap may be provided on the outer ring side of the bearings 11 and 14, or a gap may be provided on the inner ring side or the outer ring side of the bearings 37 and 38 rotatably supported around the driven rotation axis CL2.

  Further, as shown in FIG. 12, when a gap is provided in the bearing, an elastic member 18 such as an O-ring may be disposed in the gap. Thereby, the reliability can be improved by reducing the vibration of the crankpin mechanism 16 when a load is applied.

In each of the above-described embodiments, although a dual-rotating scroll compressor is used as a supercharger, the present invention is not limited to this, and any compressor that compresses fluid may be widely used. For example, it can be used as a refrigerant compressor used in an air conditioning machine.
Moreover, the double-rotating scroll compressor of the present invention can also be used as an expander.

1 Double rotation scroll compressor (Double rotation scroll fluid machine)
3 Housing 3a Motor Housing 3b Scroll Housing 3c Cooling Fin 3d Discharge Port 5 Motor (Drive)
5a Stator 5b Rotor 6 Drive shaft 7c Drive side shaft 11 Drive side bearing 15 Pin ring mechanism (synchronous drive mechanism)
15a Round hole 15b Pin member 15c Round hole 15d Rolling bearing 16 Crank pin mechanism 16a Crank pin member 16a1 First eccentric shaft portion 16a2 Second eccentric shaft portion 17a First crank pin end rolling bearing 17b Second crank pin end rolling bearing 18 O-ring (elastic member)
31 bolt (wall fixing part)
33 first support member 33a shaft portion 35 second support member 35a shaft portion 37 first support member bearing 38 second support member bearing 70 drive side scroll member 71 first drive side scroll portion 71a first drive side end plate 71b 1st drive side wall body 72 2nd drive side scroll part 72a 2nd drive side end plate 72b 2nd drive side wall body 72c 2nd drive side shaft part 72d discharge port 73 flange part 90 follower side scroll member 90h through hole 91 first follower Side scroll portion 91a first driven side end plate 91b first driven side wall 92 second driven side scroll portion 92a second driven side end plate 92b second driven side wall b base circle radius C1, C2 base circle CL1 drive side rotation axis CL2 Drive side rotation axis t1 Clearance δ Clearance Δ Initial clearance Δmin Minimum clearance ss Rotational axis distance pp Rotation radius

Claims (6)

A drive side scroll member having a spiral drive side wall body which is rotationally driven about the drive side rotation axis by the drive portion and installed at a predetermined angular interval around the center of the drive side end plate;
The driven side wall body has a spiral driven side wall body which is rotationally driven about the driven side rotation axis, is installed with a predetermined angle interval around the center of the driven side end plate, and corresponds to each of the driving side wall bodies. A driven scroll member that forms a compression space by meshing each with the corresponding drive side wall;
A plurality of synchronous drive mechanisms for transmitting the driving force from the drive side scroll member to the driven side scroll member so that the drive side scroll member and the driven side scroll member rotate at the same angular velocity in the same direction;
Equipped with
A distance between rotation axes ρs, which is a distance between the drive side rotation axis and the driven side rotation axis, and a rotation radius pp of the synchronous drive mechanism,
ρs <ρp
A dual-rotating scroll type fluid machine characterized by satisfying the following relationship. The theoretical theoretical radius ρth of engagement between the drive side wall and the driven side wall and the distance ρs between the rotation axes are
ρth> ρs
The twin-rotating scroll fluid machine according to claim 1, satisfying the following relationship:   The rotation radius pp is such that the minimum gap Δmin between the drive side wall and the driven side wall is larger than 0 when the drive side scroll member and the driven side scroll member are relatively twisted. The twin-rotating scroll type fluid machine according to claim 2, wherein The drive side wall body and the driven side wall body are respectively formed by involute curves having a base circle radius b,
When the distance between the center point of the rotation radius pp and the midpoint between the drive side rotation axis and the driven side rotation axis is Rsp,
pp <ρs + Rsp × (ρth-ρs) / b
The twin-roll scroll type fluid machine according to claim 3, wherein A drive side scroll member having a spiral drive side wall body which is rotationally driven about the drive side rotation axis by the drive portion and installed at a predetermined angular interval around the center of the drive side end plate;
The driven side wall body has a spiral driven side wall body which is rotationally driven about the driven side rotation axis, is installed with a predetermined angle interval around the center of the driven side end plate, and corresponds to each of the driving side wall bodies. A driven scroll member that forms a compression space by meshing each with the corresponding drive side wall;
A plurality of synchronous drive mechanisms for transmitting the driving force from the drive side scroll member to the driven side scroll member so that the drive side scroll member and the driven side scroll member rotate at the same angular velocity in the same direction;
Equipped with
The synchronous drive mechanism includes a crankpin having a first eccentric shaft portion and a second eccentric shaft portion having eccentric axes eccentric to each other, an end portion of each of the eccentric shaft portions, the drive side scroll member and the driven side scroll member A crank mechanism including a first crank pin end rolling bearing and a second crank pin end rolling bearing provided between the
A distance between rotation axes ρs, which is a distance between the drive side rotation axis and the driven side rotation axis, and a rotation radius pp of the synchronous drive mechanism,
ρs = ρp
Meet the relationship of
A two-turn scroll type fluid machine characterized in that a gap is provided at a position where the first crank pin end rolling bearing and / or the second crank pin end rolling bearing is fitted.   The both-rotating scroll type fluid machine according to claim 5, wherein an elastic member is disposed in the gap.

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