JP5155942B2 - Scroll type fluid machinery - Google Patents

Description

  The present invention relates to a scroll type fluid machine, and more particularly, to a rotation prevention mechanism for a movable scroll provided to form a compression mechanism of the scroll type fluid machine.

  In general, a compression mechanism and an expansion mechanism in a scroll-type compressor and an expander are formed by a combination of a fixed scroll and a movable scroll. The movable scroll is provided so that it can revolve and cannot rotate with respect to the fixed scroll. As described above, several types of rotation preventing mechanisms for making the movable scroll impossible to rotate are known.

  For example, in the scroll type fluid machine described in Patent Document 1, the orbiting pin protruding from the orbiting scroll and the housing pin protruding from the fixed scroll are provided on the protrusion restraining member that limits the relative distance between the two pins. The rotation of the orbiting scroll is prevented by sliding contact with the inner peripheral surfaces of the two holes formed.

  Further, in the scroll compressor described in Patent Document 2, the movable pin member protruding from the movable scroll and the fixed pin member protruding from the fixed scroll are in contact with each other in pairs, The rotation of the movable scroll is prevented.

Japanese Patent No. 4088392 Japanese Patent No. 3337831

  In the rotation preventing mechanism of the scroll type fluid machine described in Patent Document 1, since the turning radius is restricted on the turning pin side of the protrusion restraining member, the area swept when the protrusion restricting member rotates increases, and the thrust bearing It was difficult to enlarge. Further, since tensile stress acts on the protrusion restraining member, it is not possible to use a material that is easily damaged by pulling, such as various resins, light alloys, and sintered materials, which causes a high cost. Furthermore, when assembling the orbiting scroll and the fixed scroll, it is necessary to perform a complicated operation of fitting the pin into the hole, which hinders improvement in workability, and the lubricating oil flows between the pin and the protrusion restraining member. It was difficult to form a route.

  Further, in the rotation prevention mechanism of the scroll compressor described in Patent Document 2, as a result of contact pressure between the movable pin member and the fixed pin member, the surface pressure is increased, so that the oil film is likely to be cut. Wear was likely to occur.

  In view of the above-described problems, an object of the present invention is to provide a scroll type fluid machine including an autorotation prevention mechanism using an inexpensive member and having excellent durability.

  In order to solve the above problems, a scroll type fluid machine according to the present invention includes a fixed scroll having a spiral body standing on one end face of an end plate and a movable scroll having a spiral body standing on one end face of the end plate. Are scroll-type fluid machines that are arranged eccentrically with respect to each other and arranged in phase with each other so that the spiral bodies are meshed with each other, and the movable scroll is swiveled with respect to the fixed scroll. A movable side pin protruding from the other end surface of the scroll end plate, a fixed side pin protruding from the housing side to the other end surface side of the end plate of the movable scroll, and a rotation prevention pinched from both sides by the movable side pin and the fixed side pin. It consists of what is provided with the rotation prevention mechanism comprised by the member.

  According to the scroll type fluid machine of the present invention, the fixed side pin and the movable side pin support the rotation preventing member so as to sandwich the rotation preventing member from both sides. Since only this works, the rotation prevention member can be manufactured at low cost by sintering or the like. Further, since the rotation preventing member can be formed extremely small, the centrifugal force can be suppressed small, and noise generated by the vibration of the device can be reduced.

  In the scroll type fluid machine of the present invention, it is preferable that the rotation preventing member has a movable side recess that engages with the movable side pin and a fixed side recess that engages with the fixed side pin. Since no tensile stress acts on the rotation prevention member, the engagement destination of the movable side pin or the fixed side pin does not need to be a hole. Therefore, by forming the rotation prevention member so as to have at least a recess, the rotation prevention member Can be reduced in size and weight.

  Moreover, in such a scroll type fluid machine according to the present invention, at least one of the movable side recess and the fixed side recess may form a part of a hole provided in the rotation preventing member. As described above, since at least one of the concave portions forms a part of the hole, it is possible to facilitate the operation of fitting the rotation preventing member and the movable side concave portion or the fixed side concave portion.

  In the scroll fluid machine of the present invention, the depth of the movable side recess and / or the fixed side recess is the minimum value (Lor) of the center distance (L) between the movable side pin and the fixed side pin. It is preferable that the radius is set to be smaller than the turning radius (AOR). As described above, since the depth of the recess is set so that Lor <AOR, even if the accuracy of the parts is slightly worse and there is some error in the dimensions, the operation such as pin engagement and sliding Therefore, even when an abnormality such as liquid compression or foreign object biting occurs, excessive load is prevented and durability of the rotation prevention mechanism is ensured. Furthermore, it is preferable that a difference between a minimum value (Lor) of a center distance (L) between the center of the movable side pin and the fixed side pin and a turning radius (AOR) of the movable scroll is 0.1 mm or less. In other words, the rotation prevention mechanism is formed so that the magnitude relationship of Lor <AOR ≦ Lor + 0.1mm is established, so that smooth scrolling can be performed without being affected by the dimensional accuracy of the parts. It is possible to realize a scroll type fluid machine that has excellent durability and low noise.

  In the scroll type fluid machine of the present invention, the difference between the minimum value (Lor) of the distance (L) between the center of the movable side pin and the center of the fixed side pin and the turning radius (AOR) of the movable scroll is It is preferable that the difference is set smaller than the difference between the depth (B1) of the movable side recess and the shaft radius (R1) of the movable side pin. That is, by forming the rotation prevention mechanism so that the magnitude relationship of AOR-Lor ≦ B1-R1 is established, the rotation prevention member can be reliably clamped by the movable side pin and the fixed side pin. In addition, since the depth of the movable side recess is sufficiently larger than the shaft radius of the movable side pin, the contact range between the movable side pin and the movable side recess can be set wide, and the surface pressure is kept low and the oil film is cut. It becomes possible to prevent.

  The same can be said for the fixed side. That is, in the scroll type fluid machine of the present invention, the difference between the minimum value (Lor) of the distance (L) between the center of the movable pin and the center of the fixed pin and the turning radius (AOR) of the movable scroll is It is preferable that the distance is set smaller than the difference between the depth (B2) of the fixed-side recess and the shaft radius (R2) of the fixed-side pin. That is, by forming the rotation prevention mechanism so that the magnitude relationship of AOR-Lor ≦ B2-R2 is established, the rotation prevention member can be securely clamped by the movable side pin and the fixed side pin. Moreover, since the depth of the fixed-side recess is larger than the shaft radius of the fixed-side pin, the contact range between the fixed-side pin and the fixed-side recess can be set wide, and the surface pressure is kept low to prevent oil film breakage. It becomes possible.

In the scroll type fluid machine of the present invention, the movable side pin and the fixed side pin have a plurality of arrangement pitch circles on the circumference so as to draw an arrangement pitch circle having the same arrangement pitch angle (Ap) and the same diameter (Dp). It is preferable that they are arranged. As described above, a set of rotation prevention elements including the movable side pin, the fixed side pin, and the rotation prevention member are provided on the circumference along the circumference of the scroll, thereby effectively and smoothly preventing the rotation of the movable scroll. Can be performed. In particular, when the fixed-side pin or the movable-side pin is disposed by a predetermined angle (θ) satisfying Equation 1 in a direction that reduces the twist of the movable scroll with respect to the fixed scroll, More effective rotation prevention can be realized. In an actual scroll type fluid machine, there are tolerances related to each of a plurality of sets of fixed side pins, movable side pins, and rotation prevention members, and θ is set in a range where interference does not occur in consideration of this variation.
[Formula 1]
θ ≦ 2 · tan ⁻¹ [(AOR−Lor) / Dp]

  In such a scroll type fluid machine of the present invention, for one rotation prevention member, the initial value of the center-to-center distance (L) between the fixed side pin and the movable side pin is set to the minimum value (Lor), With respect to any other rotation prevention member, the fixed scroll and the fixed scroll are set so that an initial value of a center distance (L) between the fixed pin and the movable pin is set equal to a turning radius (AOR) of the movable scroll. It is preferable that the movable scroll is assembled. The holding state of the rotation prevention member held between the movable side pin and the fixed side pin forms a constant cycle while shifting in a form of being forwardly fed to the adjacent rotation prevention element as the movable scroll turns. As described above, the fixed scroll and the movable scroll are set to the minimum value (Lor) while the center distance (L) between the fixed side pin and the movable side pin is set to the minimum value (Lor) for one rotation prevention member. One of the rotation prevention members is assembled in a state in which the center distance (L) between the fixed side pin and the movable side pin is set equal to the turning radius (AOR) of the movable scroll, and this state is movable as an initial state. By starting the scroll turning operation, the transition between the rotation preventing members is smoothly performed. As a result, the turning operation of the movable scroll is performed smoothly.

  In the scroll type fluid machine according to the present invention, the axial thickness of the rotation preventing member is within a range in which a gap larger than the oil film thickness is secured with respect to the axial interval between the movable scroll and the housing and does not interfere with a dimensional tolerance. A maximum value is preferred. Thus, according to the scroll type fluid machine of the present invention, the axial thickness of the rotation prevention member can be maximized as long as there is no problem in the turning operation of the movable scroll. The durability can be easily increased.

  As described above, according to the scroll type fluid machine according to the present invention, since the rotation preventing member is configured to generate only the compressive stress, the rotation preventing member can be manufactured by sintering and the cost can be reduced. It becomes. Further, the rotation preventing member can be designed to be extremely small, and a scroll type fluid machine having a small centrifugal force and improved vibration noise can be realized. Furthermore, by reducing the size of the rotation prevention member, the range that does not interfere with the rotation prevention member is expanded, so that the weight of the counterweight can be easily secured.

  In the scroll type fluid machine according to the present invention, since it is easy to widen the contact surface between the movable side pin or the fixed side pin and the rotation prevention member, the rotation of the oil film is difficult to occur at a low surface pressure and excellent in durability. A blocking mechanism can be easily realized. In addition, by forming the movable side recess of the rotation preventing member that engages with the movable side pin so as to open outward, the work when the movable scroll is assembled to the fixed scroll can be facilitated.

  In the scroll type fluid machine according to the present invention, since the minimum turning radius is determined only from the structure of the rotation prevention mechanism, the eccentric bush can be eliminated. In addition, by setting the dimension of the rotation prevention member within a predetermined range, smooth operation can be performed without being affected by the dimensional accuracy of the parts, and even when abnormal conditions such as liquid compression or foreign object biting occur, an excessive load It is possible to realize a scroll type fluid machine that does not generate turbulence and ensures durability.

It is a longitudinal section showing a compressor concerning one embodiment of the present invention. It is a cross-sectional view which shows the rotation prevention mechanism of the compressor of FIG. It is explanatory drawing for demonstrating the shift | offset | difference of a movable scroll arrangement | positioning angle which arises by the autorotation force which acts on the movable scroll of FIG. It is a top view which shows the rotation prevention member for preventing rotation of the movable scroll of FIG. 1, (A) is an example in which both recessed parts do not form a part of hole, (B) is one side of a recessed part having a hole. This is an example of forming a part. It is a cross-sectional view showing a rotation prevention mechanism of a scroll compressor according to another embodiment of the present invention. It is a cross-sectional view which shows the rotation prevention mechanism of the scroll compressor which concerns on the further another embodiment of this invention.

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows an entire scroll compressor 1 according to an embodiment of the present invention. In FIG. 1, the compression mechanism 2 includes a fixed scroll 3 composed of a spiral body and a movable scroll 4 composed of a spiral body and an end plate 5. The movable scroll 4 is turned with respect to the fixed scroll 3 in a state in which the rotation is blocked by the rotation blocking element 36 including the rotation blocking member 31, the fixed side pin 34 and the movable side pin 35. During operation of the compressor 1, the main shaft 8 (rotary shaft) is driven to rotate, and via the eccentric pin 9 disposed on one end side of the main shaft 8 and the eccentric bush 10 rotatably engaged with the main shaft 8. Is converted into a turning motion of the movable scroll 4. Then, the refrigerant sucked as the fluid to be compressed is guided to the compression mechanism 2 and compressed, and sent from the casing 6 to the outside of the compressor 1 through the discharge hole 13 and the discharge chamber 14.

  FIG. 2 is a cross-sectional view showing a rotation prevention mechanism of the compressor 1 of FIG. In the compressor housing 6, the fixed scroll 3 and the movable scroll 4 are assembled so that the respective spiral bodies are engaged with each other to form the compression mechanism 2. The movable scroll 4 orbits around the central axis of the fixed scroll 3 that is always stationary with a predetermined orbiting radius (AOR). As the orbiting scroll 4 turns, the fluid to be compressed such as refrigerant is compressed.

  The movable scroll 4 includes a movable side pin 35 (35a to 35d) projecting from a surface of the end plate 5 opposite to the fixed scroll 3 and a movable side pin 35 (35a to 35d) in the housing 6. ) And the rotation prevention member 31 (31a to 31d) are prevented from rotating. The rotation preventing member 31 (31a to 31d) having a substantially H-shaped planar shape includes a fixed recess 32 (32a to 32d) that engages with the fixed pin 34 (34a to 34d) and a movable pin 35 ( 35a-35d) is provided with a movable side recess 33 (33a-33d), which is sandwiched between the movable side pin 35 (35a-35d) and the fixed side pin 34 (34a-34d).

  In the present embodiment, the fixed side pin 34 and the movable side pin 35 draw an arrangement pitch circle having an equal diameter (Dp) on the end plate 5 of the movable scroll 4 at an arrangement pitch angle of 90 degrees. Is arranged. The fixed-side pin 34 and the movable-side pin 35 arranged in this way constitute a rotation prevention element 36 (36a to 36d) between the rotation prevention member 31 held between them. A combination of such rotation prevention elements 36 forms a rotation prevention mechanism for the movable scroll 4.

  In the present embodiment, the distance between the fixed side pin 34 and the movable side pin 35 in one rotation prevention element 36 is not completely constant, and some play is provided. For example, as shown in FIG. 2, a slight gap is formed between the movable side pins 35b to 35d and the rotation prevention members 31b to 31d. In particular, the distance between the fixed side pin 34c and the movable side pin 35c is relatively large. On the other hand, no gap is formed between the fixed side pin 34a and the movable side pin 35a and the rotation prevention member 31a. Thus, the minimum value (Lor) of the center-to-center distance (L) between the fixed side pin 34 and the movable side pin 35 is determined by appropriately setting the depth (B) of the rotation preventing member 31. The center-to-center distance (L) between the fixed side pin 34 and the movable side pin 35 is preferably set so that the above-described slight play occurs. Specifically, the depth (B) of the rotation preventing member 31 is set so that the minimum value (Lor) of the center distance (L) is smaller than the turning radius (AOR) of the movable scroll 4. It is preferable. However, if the difference between Lor and AOR is too large, smooth turning operation of the movable scroll 4 is hindered, and therefore the difference is preferably within 0.1 mm at the maximum.

  As shown in FIG. 2, when the fixed scroll 3 and the movable scroll 4 are assembled, the center distance (L) takes the minimum value (Lor) in the rotation prevention element 36a, and the rotation prevention element 36a. It is preferable that the rotation preventing element 36c located at the farthest position is assembled in an initial state so as to be equal to the turning radius (AOR) of the movable scroll 4. If the play of the center distance (L) is dispersed in the rotation prevention elements 36a to 36d in the initial state, the center distance (L) assumed from the depth (B) of the rotation prevention member 31. This play may not be fully utilized during the turning operation of the movable scroll 4. Therefore, the line segment connecting the movable pin 35a and the movable pin 35c (length = Dp) is as follows with respect to the line segment connecting the fixed pin 34a and the fixed pin 34c (length = Dp). It is preferable that the angle α satisfying Expression 2 is assembled. By arranging the movable side pins 35a to 35d and the fixed side pins 34a to 34d so that such a relational expression is satisfied, the cycle of the pinching state of the rotation prevention members 31a to 31d can be smoothly shifted. Become. Moreover, since the rotation prevention member 31 of this embodiment can be formed very compactly, even if it employ | adopts a comparatively large counterweight 37, it is hard to interfere with the rotation prevention member 31. FIG.

[Formula 2]
tan α = (AOR−Lor) / Dp

  Note that the angle α in the above formula 2 is specifically a small angle of less than 0.2 degrees, for example. When the compressor 1 is in operation, a rotating force acts on the movable scroll 4. The fixed side pin 34 and the movable side pin 35 use this rotation force to prevent the rotation of the movable scroll 4 by holding the rotation prevention member 32 at one or more locations on the circumference of each arrangement pitch circle. doing. FIG. 3 shows a state in which the fixed side pin 34 and the movable side pin 35 are displaced by a predetermined angle (θ) in the direction of reducing the twist of the movable scroll 4 with respect to the fixed scroll 3 due to such rotation force. I will explain.

  FIG. 3 is an explanatory diagram for explaining the shift in the movable scroll arrangement angle caused by the rotation force acting on the movable scroll in FIG. 1. When the scroll of the movable scroll 4 is prevented from rotating and the swirl wall of the movable scroll 4 is swung while being in contact with the swirl wall of the fixed scroll 3, the movable scroll 4 has an amplitude equal to the swivel radius (AOR) in the axis Y direction. Will reciprocate. In this case, the distance connecting the center O of the arrangement pitch circle 38 of the movable side pin 35 and the center of the arrangement pitch circle of the fixed side pin 34 is determined by the presence of the rotation preventing members 31a to 31d. It is never smaller than the minimum value (Lor) of the center-to-center distance (L) of 35. Further, the arrangement pitch circle of the fixed pins 34 has substantially the same diameter (Dp) as the arrangement pitch circle 38 of the movable pins 35. The condition that the predetermined angle (θ) at which the movable scroll 4 rotates by the rotation force acting on the movable scroll 4 is as shown in the above-mentioned formula 1. Here, since the predetermined angle (θ) is in the relationship between the central angle and the circumferential angle with respect to the same arc with respect to the angle α in Equation 2, it is clear from FIG. 3 that the relationship of θ = 2α is established. is there.

[Formula 1]
θ ≦ 2 · tan ⁻¹ [(AOR−Lor) / Dp]

  FIG. 4 is a plan view showing a rotation prevention member 31 for preventing the rotation of the movable scroll 4 of FIG. 1. FIG. 4A is a plan view in which both the fixed side recess 32 and the movable side recess 33 form part of the hole. (B) shows an example in which only the movable-side concave portion 33 forms a part of the hole. As shown in FIG. 4A, in this embodiment, since the tensile stress does not act on the rotation preventing member 31, both the fixed-side concave portion 32 and the movable-side concave portion 33 are fixed even if both concave portions are open. The rotation preventing member 31 can be clamped by the side pin 34 and the movable side pin 35. In particular, since the depth (B) of the recess is set to be larger than the axial radius (R) of the fixed side pin 34 or the movable side pin 35, the rotation prevention member 31 is fixed by the fixed side pin 34 and the movable side pin 35. Can be clamped more reliably. Further, the difference between the minimum value (Lor) of the center-to-center distance (L) and the turning radius (AOR) of the movable scroll 4 is such that the depth (B1) of the movable-side recess 33 and the axial radius (R1) of the movable-side pin 35 When the movable scroll 4 is turned, the movable pin 35 can be more reliably engaged with the movable concave portion 33 of the rotation preventing member 31. The same applies to the fixed side, and the difference between the minimum value (Lor) of the center-to-center distance (L) and the turning radius (AOR) of the movable scroll 4 is the depth (B2) of the fixed side recess 32 and the fixed side pin. By setting it smaller than the axial radius (R2) of 34, the fixed-side pin 34 can be more reliably engaged with the fixed-side recess 32 of the rotation preventing member 31 when the movable scroll 4 is turned.

  Further, as shown in FIG. 4B, holes may be formed in the rotation preventing member 41 by closing both ends of the recessed portion of the fixed-side recessed portion 32. Thus, when either the fixed side recess 32 or the movable side recess 33 forms a part of the hole, the fixed side pin 34 can be passed through the hole when the movable scroll 4 is assembled to the fixed scroll 3. Therefore, the assembling work can be facilitated.

  FIG. 5 is a cross-sectional view showing a rotation prevention mechanism of a scroll compressor according to another embodiment of the present invention. The rotation prevention member 31 (31a to 31d) of FIG. 2 is replaced with the rotation of FIG. 4 (B). The blocking member 41 (41a to 41d) is replaced. Since the other points are the same as those in FIG. 2, the same reference numerals are attached and the description is omitted, and the same applies to the following embodiments. Thus, the assembling property of the scroll compressor can be improved by forming a part of the hole in the fixed recess 32.

  FIG. 6 is a cross-sectional view showing a rotation prevention mechanism of a scroll compressor according to still another embodiment of the present invention. The rotation prevention member 51 (51a to 51d) of this embodiment has a shape in which the fixed-side recess 32 and the movable-side recess of the rotation prevention member 41 of FIG. That is, contrary to the rotation preventing member 41 in FIG. 4B, both ends of the recessed portion of the fixed-side recessed portion 32 are opened, and both ends of the recessed portion of the movable-side recessed portion 33 are closed. As described above, even when the movable-side concave portion 33 forms part of the hole, the assembly of the scroll compressor is improved as in the case where the fixed-side concave portion 32 forms part of the hole. Is planned.

  The scroll type compressor according to the present invention is applicable to any type of scroll type compressor having a rotation prevention mechanism using a rotation prevention member.

1 Compressor 2 Compression mechanism 3 Fixed scroll 4 Moveable scroll
5 End plate 6 Casing 7 Housing 8 Main shaft 9 Eccentric pin 10 Eccentric bush 13 Discharge hole 14 Discharge chamber 31, 41, 51, 31a, 31b, 31c, 31d Rotation prevention member 32 Fixed side concave portion 33 Movable side concave portion 34, 34a, 34b , 34c, 34d Fixed side pins 35, 35a, 35b, 35c, 35d Movable side pins 36, 36a, 36b, 36c, 36d Rotation prevention element 37 Counterweight 38 Arrangement pitch circle

Claims (11)

  The fixed scroll in which the spiral body is erected on one end surface of the end plate and the movable scroll in which the spiral body is erected on the one end surface of the end plate are decentered from each other and the phases are shifted, and the spiral bodies are A scroll-type fluid machine that is arranged to mesh with each other and that orbits the movable scroll with respect to the fixed scroll, the movable side pin protruding from the other end surface of the end plate of the movable scroll, and the housing side A rotation-preventing mechanism comprising a fixed-side pin projecting to the other end surface side of the end plate of the movable scroll, and a rotation-preventing member sandwiched from both sides by the movable-side pin and the fixed-side pin is provided. Scroll type fluid machine.   2. The scroll fluid machine according to claim 1, wherein the rotation preventing member has a movable side recess that engages with the movable side pin and a fixed side recess that engages with the fixed side pin.   The scroll type fluid machine according to claim 2, wherein at least one of the movable side recess and the fixed side recess forms a part of a hole provided in the rotation prevention member.   The depth of the movable recess and / or the fixed recess is such that the minimum value (Lor) of the center distance (L) between the movable pin and the fixed pin is smaller than the turning radius (AOR) of the movable scroll. The scroll type fluid machine according to claim 2 or 3, wherein the scroll type fluid machine is set.   The difference between the minimum value (Lor) of the center distance (L) between the center of the movable side pin and the fixed side pin and the turning radius (AOR) of the movable scroll is 0.1 mm or less. Scroll type fluid machine.   The difference between the minimum value (Lor) of the distance (L) between the center of the movable pin and the fixed pin and the turning radius (AOR) of the movable scroll is the depth of the movable recess (B1). 6. The scroll fluid machine according to claim 4, wherein the scroll type fluid machine is set to be smaller than a difference between an axis radius of the movable side pin and a shaft radius of the movable side pin.   The difference between the minimum value (Lor) of the center distance (L) between the center of the movable pin and the fixed pin and the turning radius (AOR) of the movable scroll is the depth of the fixed recess (B2). The scroll type fluid machine according to any one of claims 4 to 6, wherein the scroll type fluid machine is set to be smaller than a difference between a shaft radius (R2) of the fixed side pin.   A plurality of the movable side pins and the fixed side pins are arranged on the circumference so as to draw an arrangement pitch circle having an arrangement pitch angle (Ap) equal to each other and a diameter (Dp) equal to each other. A scroll type fluid machine according to any one of the above. 9. The scroll according to claim 8, wherein the fixed-side pin or the movable-side pin is arranged so as to be shifted by a predetermined angle (θ) that satisfies Equation 1 in a direction that reduces the twist of the movable scroll with respect to the fixed scroll. Type fluid machine.
[Formula 1]
θ ≦ 2 · tan ⁻¹ [(AOR−Lor) / Dp]   For one rotation prevention member, the initial value of the center-to-center distance (L) between the fixed side pin and the movable side pin is set to the minimum value (Lor), and for any other rotation prevention member, the fixed side pin The fixed scroll and the movable scroll are assembled so that an initial value of a center-to-center distance (L) between the pin and the movable pin is set equal to a turning radius (AOR) of the movable scroll. A scroll type fluid machine according to any one of the above.   The axial thickness of the rotation preventing member is a maximum value within a range in which a gap equal to or larger than an oil film thickness is secured with respect to an axial interval between the movable scroll and the housing and interference does not occur due to a dimensional tolerance. The scroll type fluid machine according to any one of the above.

Images