Fluid transfer device, coating device including same, and coating method

Abstract

To provide a fluid transfer device which causes a male screw shaped rotor to rotate eccentrically in a stator having a female screw shaped insertion hole to solve a problem of pulsation occurring when a liquid material is discharged from a nozzle, and to provide an application device including the device and an application method.SOLUTION: A fluid transfer device 1 includes: an external cylinder 10; a stator 11 having a female screw shaped insertion hole 12 being a through hole provided on an inner peripheral surface of the external cylinder; and a male screw shaped rotor 20 which is connected to a rotor drive part and eccentrically rotates while contacting with an inner peripheral surface of the stator 11. The rotor 20 inserted into the insertion hole 12 is rotated to transfer a fluid in a transfer passage formed by the stator 11 and the rotor 20. An adhesive force for adhering to the rotor 20 in an inlet portion and an outlet portion of the stator 11 is smaller than an adhesive force for adhering to the rotor 20 in a center portion of the stator 11.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a fluid transfer device capable of delivering a fluid by eccentrically rotating a male-screw rotor that abuts against the inner peripheral surface of a stator, a coating device including the same device, and a coating method. [Background technology]

[0002] Conventionally, there has been known a device for conveying liquid materials or fluids, which includes a rotor that is a single-axis eccentric screw and a stator through which the rotor is inserted. This type of device is also called a single-axis eccentric screw pump or a mono pump. The stator of this device has an interference that elastically deforms with the rotation of the rotor, and the elastic action of the stator is used to convey the liquid material or fluid.

[0003] For example, Patent Document 1 discloses a fluid transport device in which the volume of the transport space formed by the through holes in the stator is reduced in the flow direction from the suction port to the discharge port in order to solve the problem of air bubble generation that occurs when discharging highly volatile liquids or liquids with a large amount of dissolved gas.

[0004] Furthermore, Patent Document 2 discloses a single-shaft eccentric screw pump in which the interference on the discharge port side is smaller than the interference on the suction port side in order to prevent problems such as cracking or breakage of the stator that occur when the volumetric efficiency of the fluid transport path is less than 1 and the pump is used under conditions where the discharge pressure is high. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Patent No. 5802914 [Patent Document 2] Japanese Patent Application Laid-Open No. 2010-248979 Summary of the Invention [Problem to be solved by the invention]

[0006] However, the devices disclosed in the above documents have the problem that pulsation occurs when the fluid is discharged from the discharge port, making it impossible to discharge a fixed amount uniformly. When the devices of the above documents are incorporated into a fluid circulation circuit and used as a circulation pump, there is a problem that pulsation occurs in the flow of fluid in the circulation circuit, making the flow unstable. When the liquid material is discharged onto the surface of a workpiece using the devices disclosed in the above documents, if pulsation occurs when drawing a line on the surface of the workpiece, the line width becomes non-uniform, which is a problem.

[0007] Therefore, an object of the present invention is to provide a fluid transfer device that can solve the problem of pulsation that occurs when a fluid is discharged by eccentrically rotating a male-threaded rotor within a stator having a female-threaded insertion hole, an application device that includes the same device, and an application method. [Means for solving the problem]

[0008] The fluid transfer device of the present invention comprises an outer cylinder and a fluid transfer member on the inner circumferential surface of the outer cylinder. , and its outer surface is tightly attached a rotor connected to a rotor drive unit and rotating eccentrically while abutting against the inner peripheral surface of the stator; and a rotor having a male screw shape, which is inserted into the insertion hole and rotates eccentrically, thereby transferring a fluid in a conveying path formed by the stator and the rotor. The stator is configured to have an inlet portion that occupies a certain range in the longitudinal direction from the inlet of the conveying path, an outlet portion that occupies a certain range in the longitudinal direction from the outlet of the conveying path, and a central portion located between the inlet portion and the outlet portion, and is configured so that the adhesion force of the rotor at the inlet portion and the outlet portion of the stator is smaller than the adhesion force of the rotor at the central portion.

[0009] In the above-described fluid transfer device, the amount of interference caused by the rotor at the inlet portion and the outlet portion of the stator may be configured to be smaller than the amount of interference caused by the rotor at the central portion, thereby making the adhesion force caused by the rotor at the inlet portion and the outlet portion of the stator smaller than the adhesion force caused by the rotor at the central portion. The above-described fluid transfer device may be characterized in that an interference amount by the rotor is gradually reduced from the central portion toward the outlet or inlet. In the above-described fluid transfer device, the central portion may be characterized in that the contact force exerted by the rotor is uniform throughout the longitudinal direction. In the above-mentioned fluid transfer device, (A) when the adhesion force between the rotor and the stator at the inlet of the conveying path is A1, the adhesion force between the rotor and the stator at a position one turn of the rotor from the inlet of the conveying path is A2, the adhesion force between the rotor and the stator at a position between the inlet of the conveying path and the position one turn of the rotor from the inlet of the conveying path is A3, and the adhesion force between the rotor and the stator at a central portion in the longitudinal direction of the conveying path is A4, a relationship of A4>A2>A3>A1 is satisfied; and / or (B) It may be characterized in that, when the adhesion force between the rotor and the stator at the outlet of the conveying path is B1, the adhesion force between the rotor and the stator at a position one turn of the rotor from the outlet of the conveying path is B2, the adhesion force between the rotor and the stator at a position between the outlet of the conveying path and a position one turn of the rotor from the outlet of the conveying path is B3, and the adhesion force between the rotor and the stator at the longitudinal center part of the conveying path is B4, the relationship is B4>B2>B3>B1. In the above-described fluid transfer device, the amount of interference by the rotor may be uniform across the longitudinal center portion of the insertion hole.

[0010] In the above-mentioned fluid transfer device, (A) when an interference amount between the rotor and the stator at the inlet of the conveying path is A1, an interference amount between the rotor and the stator at a position one turn of the rotor from the inlet of the conveying path is A2, an interference amount between the rotor and the stator at a position between the inlet of the conveying path and a position one turn of the rotor from the inlet of the conveying path is A3, and an interference amount between the rotor and the stator at a central portion in the longitudinal direction of the conveying path is A4, a relationship of A4>A2>A3>A1 is satisfied; and / or (B) When the interference amount between the rotor and the stator at the outlet of the conveying path is B1, the interference amount between the rotor and the stator at a position one turn of the rotor from the outlet of the conveying path is B2, the interference amount between the rotor and the stator at a position between the outlet of the conveying path and the position one turn of the rotor from the outlet of the conveying path is B3, and the interference amount between the rotor and the stator at the center portion of the longitudinal direction of the conveying path is B4, the relationship may be B4>B2>B3>B1. In the above-described fluid transfer device, the central portion of the insertion hole in the longitudinal direction may extend over an area equivalent to two or more turns of the rotor. In the above-mentioned fluid transfer device, the inlet portion may be in a range of more than one turn of the rotor from the inlet of the conveying path, and the outlet portion may be in a range of more than one turn of the rotor from the outlet of the conveying path. In the above-described fluid transfer device, the longitudinal extent of the central portion of the stator may be longer than the longitudinal extents of the inlet portion and the outlet portion. In the above fluid transfer device, the ratio of the interference amount of the rotor at the inlet portion and the outlet portion of the stator to the interference amount of the rotor at the central portion of the stator may be 0.4 to 0.7:1.

[0011] In the above-mentioned fluid transfer device, the shape and / or material properties of the inlet portion and the outlet portion of the stator may be set to specifications different from those of the central portion so that the adhesion force between the stator and the rotor at the inlet portion and the outlet portion of the stator is smaller than the adhesion force between the stator and the rotor at the central portion of the stator. In the above-described fluid transfer device, at the inlet portion of the conveying path, one of the material properties and thickness of the stator, together with the amount of interference of the stator, is set to a specification different from that of the central portion of the insertion hole so that the adhesion force between the stator and the rotor at the inlet portion is smaller than that of the rotor at the central portion of the stator, and at the outlet portion of the conveying path, one of the material properties and thickness of the stator, together with the amount of interference of the stator, is set to a specification different from that of the central portion of the insertion hole so that the adhesion force between the stator and the rotor at the outlet portion of the stator is smaller than that of the rotor at the central portion of the stator. In the above-mentioned fluid transfer device, the longitudinal central portion of the stator may be made of a material having a stronger elastic force than the material constituting the inlet portion and / or the outlet portion of the stator.

[0012] In the above-described fluid transfer device, the inner circumferential surface of the upstream end portion and the downstream end portion of the outer cylinder may have a larger diameter than a central portion of the outer cylinder in the longitudinal direction. In the above-described fluid transfer device, a central portion in a longitudinal direction of the outer cylinder may have an inner circumferential surface with a uniform diameter. In the above-described fluid transfer device, a central portion of the outer cylinder in the longitudinal direction may have an inner peripheral surface having a female thread shape with the same pitch as that of the stator. In the above-described fluid transfer device, the outer peripheral surface of the outer cylinder may be provided with an uneven shape at a position corresponding to the inner peripheral surface of the female thread shape. In the above-mentioned fluid transfer device, the inner circumferential surface at the upstream end portion of the outer cylinder may be configured as a tapered surface that expands in diameter toward the upstream end of the outer cylinder, and the inner circumferential surface at the downstream end portion of the outer cylinder may be configured as a tapered surface that expands in diameter toward the downstream end of the outer cylinder. In the above-mentioned fluid transfer device, the outer cylinder may be characterized by having an upstream end portion inner peripheral surface having an inner peripheral surface of the same diameter, an inlet side tapered surface connecting the upstream end portion inner peripheral surface and the central portion, a downstream end portion inner peripheral surface having an inner peripheral surface of the same diameter, and an outlet side tapered surface connecting the downstream end portion inner peripheral surface and the central portion. In the above-described fluid transfer device, the range of the expanded inner circumferential surface at the upstream end portion of the outer cylinder may be longer than the range of the expanded inner circumferential surface at the downstream end portion of the outer cylinder. In the above-mentioned fluid transfer device, the ratio of the longitudinal range of the inlet portion of the stator to the longitudinal range of the central portion of the stator may be 3:5 to 10, and the ratio of the longitudinal range of the outlet portion of the stator to the longitudinal range of the central portion of the stator may be 2:5 to 10.

[0013] In the above-mentioned fluid transfer device, the stator may be characterized in that it is composed of a transport action area having an interference caused by the rotor, and a non-transport action area located upstream of the transport action area and not in contact with the rotor (having no interference). In the above-mentioned fluid transfer device, the inner surface of the insertion hole that constitutes the non-transporting action area may be configured as a tapered surface whose diameter increases from the center side of the insertion hole toward the inlet side. In the above-mentioned fluid transfer device, the volume of the non-transport action area may be smaller than the volume of any of the transport spaces within the insertion holes that are located in the transport action area and that are opened and closed by eccentric rotation of the rotor. In the above-described fluid transfer device, the adhesion force between the stator and the rotor at the inlet portion and / or the outlet portion may be weakest when the rotor is at the uppermost position and the lowermost position. The above-mentioned fluid transfer device may be a liquid material discharge device further comprising a nozzle member having a discharge port for discharging the fluid flowing out from the outlet of the transport path. In the above-described fluid transfer device, the stator may be fixed to the outer cylinder so that the relative position of the stator with respect to the outer cylinder is not displaced by the rotation of the rotor. In the above-described fluid transfer device, the outer cylinder and the stator may be fixed by adhesive.

[0014] The coating device of the present invention is a coating device including the above-described fluid transfer device and a relative movement device that moves the fluid transfer device and an object to be coated relatively to each other.

[0015] The coating method of the present invention is a method for drawing a line of uniform line width on the surface of a workpiece using the above-mentioned coating device. [Effects of the Invention]

[0016] According to the present invention, it is possible to solve the problem of pulsation occurring in the discharged fluid when the rotor is rotated eccentrically within the stator to discharge the fluid. [Brief explanation of the drawings]

[0017] [Figure 1] 1 is a cross-sectional side view of a main part of a liquid material discharge device according to a first embodiment. [Figure 2] 1A and 1B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a first embodiment, in which (a) is a side cross-sectional view when the rotor is at the top position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder, and (f) is a rear view of only the outer cylinder. [Figure 3] FIG. 1(a) is a cross-sectional view of an outer cylinder, a stator, and a rotor according to the prior art, and FIG. 1(b) is a cross-sectional view of an outer cylinder, a stator, and a rotor according to the first embodiment. [Figure 4] 4A and 4B are cross-sectional views illustrating interference of a stator according to a first embodiment, where FIG. 4A is a front cross-sectional view of an inlet portion of the stator, and FIG. 4B is a front cross-sectional view of a central portion of the stator in the longitudinal direction. [Figure 5]1A and 1B are cross-sectional views of an outer cylinder, a stator, and a rotor according to a first embodiment, in which (a) is a side cross-sectional view and a front cross-sectional view when the rotor is at a 0° position, (b) is a side cross-sectional view and a front cross-sectional view when the rotor is at a 90° position, (c) is a side cross-sectional view and a front cross-sectional view when the rotor is at a 180° position, (d) is a side cross-sectional view and a front cross-sectional view when the rotor is at a 270° position, and (e) is a side cross-sectional view and a front cross-sectional view when the rotor is at a 360° position. [Figure 6] This is a comparison diagram explaining the formation of the transfer space from 0° to 90° in a configuration with a small stator interference (left figure) and a configuration with a large interference (right figure), where (a) is a front cross-sectional view when the rotor is at 0°, (b) is a front cross-sectional view when the rotor has rotated from (a), (c) is a front cross-sectional view when the rotor has rotated further from (b), and (d) is a front cross-sectional view when the rotor is at 90°. [Figure 7] This is a comparison diagram explaining the formation of the transfer space from 270° to 360° in a configuration with a small stator interference (left figure) and a configuration with a large interference (right figure), where (a) is a front cross-sectional view when the rotor is at 270°, (b) is a front cross-sectional view when the rotor has rotated from (a), (c) is a front cross-sectional view when the rotor has rotated further from (b), and (d) is a front cross-sectional view when the rotor is at 360° (0°). [Figure 8] 10A and 10B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a second embodiment, in which (a) is a side cross-sectional view when the rotor is at the highest position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder, and (f) is a rear view of only the outer cylinder. [Figure 9] 10A and 10B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a third embodiment, in which (a) is a side cross-sectional view when the rotor is at the highest position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder, and (f) is a rear view of only the outer cylinder. [Figure 10]10A and 10B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a fourth embodiment, in which (a) is a side cross-sectional view when the rotor is at the highest position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder, and (f) is a rear view of only the outer cylinder. [Figure 11] 10A and 10B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a fifth embodiment, in which (a) is a side cross-sectional view when the rotor is at the highest position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder, and (f) is a rear view of only the outer cylinder. [Figure 12] 10A and 10B are explanatory diagrams of an outer cylinder, a stator, and a rotor according to a sixth embodiment, in which (a) is a side cross-sectional view when the rotor is at the uppermost position (0°), (b) is an AA cross-sectional view of (a), (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), and (e) is a rear view in which the rotor is omitted. DETAILED DESCRIPTION OF THE INVENTION

[0018] An embodiment of the fluid transfer device of the present invention will be described below using the example of a liquid material discharge device. However, the technical concept of the present invention is not limited to application to a liquid material discharge device, but can also be applied to, for example, a circulation pump incorporated into a fluid circulation circuit. Furthermore, the fluid transferred by the fluid transfer device is not limited to liquid materials, but can also be applied to fluids such as powders and pastes. <First embodiment> 1 is a cross-sectional side view of a main part of a liquid material discharge device 1 according to a first embodiment. For ease of explanation, the nozzle member 13 side may be referred to as the front side (front face) and the side opposite the nozzle member 13 may be referred to as the rear side (rear face) below. The liquid material discharge device 1 is configured to include a rotor drive device 3 provided on the rear side of a main body 2, and a stator unit 15 provided on the front side.

[0019] The main body 2 is hollow and houses a connecting member 4 and a shaft 5 inside. The rear end of the shaft 5 is connected to the rotor drive unit 3 via a coupling 6, so that driving force from the rotor drive unit 3 is transmitted. When the shaft 5 is rotated by the rotor drive unit 3, the rotor 20 connected via the connecting member 4 rotates eccentrically. The rotor drive unit 3 can be combined with an external general-purpose rotating device. A supply pipe 7 is connected to the top surface of the main body 2, and a liquid material is supplied from a storage container (not shown) to a liquid material supply port 8. Here, the liquid material in the storage container may be pressurized using compressed air, a piston, or the like. An air bubble vent hole 14 is provided on the top surface of the supply pipe 7. The air bubble vent hole 14 may be plugged during use. The rear end of the main body 2 is a connector 9 to which a power supply cable (not shown) is connected.

[0020] Stator unit 15 is composed of stator 11 and outer cylinder 10 that fixes stator 11. Stator unit 15 is detachably fixed to rotor drive device 3 by known means such as screws or a chuck, and even when rotor 20 rotates within stator 11 due to the drive of rotor drive device 3, there is no misalignment or rattle.

[0021] The outer cylinder 10 is a cylindrical body made of metal, ceramic, or the like, and in this embodiment, has the same thickness from the front end to the rear end. Because the outer cylinder 10 firmly secures the stator 11, even when the rotor 20 (described later) rotates within the stator 11 due to the rotor drive unit 3, the stator 11 does not slide within the outer cylinder 10 or create a gap between the outer cylinder 10 and the stator 11. The front end of the outer cylinder 10 communicates with a nozzle member 13 having a liquid material outlet (discharge port). The liquid material discharge device 1 of this embodiment is used by holding the workpiece, or the object to be coated, and the nozzle member 13 facing each other at any angle. In FIG. 1, the outer periphery of the outer cylinder 10 has a straight shape with the same diameter, but this is not limited to the illustrated shape. For example, the outer periphery may have a stepped or curved shape. Furthermore, the inner periphery of the outer cylinder 10 may be made visible by forming an outer periphery with an uneven shape that follows the unevenness of the inner periphery of the outer cylinder 10. Furthermore, the outer periphery of the outer cylinder 10 may be provided with grooves, threads, flanges, or the like. In addition, since the outer cylinder 10 and the stator 11 are depicted in simplified form in FIG. 1, detailed explanations of these will be given with reference to FIG. 2 and subsequent figures.

[0022] 2 is an explanatory diagram of the outer cylinder 10, stator 11, and rotor 20 according to the first embodiment, where (a) is a side cross-sectional view when the rotor 20 is at the uppermost position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder 10, and (f) is a rear view of only the outer cylinder 10. In Figures 2(a) and (e), the outlet of the insertion hole 12 is provided on the left end surface, and the inlet of the insertion hole 12 is provided on the right end surface.

[0023] As shown in FIG. 2(a), a stator 11 is disposed within an outer cylinder 10 in close contact with the inner circumferential surface of the outer cylinder 10. The stator 11 has an insertion hole 12 with an internally threaded inner circumferential surface, and cooperates with a rotor 20 disposed within the insertion hole 12 and having an externally threaded outer circumferential surface to form a conveying path. That is, the conveying path is a flow path formed by the stator 11 and the rotor 20, and is a flow path that is only realized when the rotor 20 is inserted into the stator 11. In FIG. 2(a), the right end of the outer cylinder 10 is the start position of the conveying path (the inlet of the conveying path), and the left end of the outer cylinder 10 is the end position of the conveying path (the outlet of the conveying path). The rotor 20, which rotates eccentrically within the insertion hole 12, and the fixed stator 11 slide in close contact with each other to form a conveying action region that acts to transport the liquid material within the conveying path. In this embodiment, the area from the right end to the left end of the insertion hole 12 constitutes a transport action area (note that the insertion hole 12 shown in FIG. 12, which will be described later, also includes a non-transport action area).

[0024] The stator 11 is an elastic body made of an elastic material such as rubber or resin. The stator 11 has an interference that causes it to elastically deform when pressed by the rotor 20 inserted into the insertion hole 12, and transports the liquid material in the insertion hole 12 by the elastic action generated by the rotation of the rotor 20. Here, the interference is the "tightening margin" and refers to the overlapping thickness (difference in dimension, amount of interference). In this embodiment, the inner circumferential surface of the stator 11 is formed into a double-threaded female thread shape, and the pitch is the same in the area where it abuts against the rotor 20. The female thread shape of the stator 11 is not limited to the illustrated two-thread shape, and can be any female thread shape. When the number of threads of the stator 11 is changed, it is set to n+1, which is one more than the number of threads n of the rotor 20. Furthermore, the winding direction of the female thread of the stator 11 may be either left-handed (left-hand thread) or right-handed (right-hand thread). In this specification, a stator that is right-handed with respect to the direction of travel of the liquid material will be described.

[0025] The rotor 20 has a single-start external thread. The rotor 20 is disposed within the insertion hole 12 of the stator 11, and dynamically forms two transport paths within the insertion hole 12 by eccentrically rotating. More specifically, in each of the two transport paths, cavities (enclosed spaces) are sequentially formed with a phase shift of 180° during the rotation cycle of the rotor 20, and the liquid material is transported as the cavities filled with the liquid material move from the inlet side to the outlet side. The rear end of the rotor 20 is connected to the shaft 5 via a connecting member 4, and the rotor 20 rotates eccentrically when the driving force from the rotor drive unit 3 is transmitted to the shaft 5. The diameter of the rotor 20 is the same and has the same pitch at least in the area where it abuts against the stator 11. The male thread shape of the rotor 20 is not limited to a single thread, and can be any male thread shape that matches the shape of the inner peripheral surface of the stator 11. In this embodiment, the male thread shape of the outer peripheral surface of the rotor 20 is described as being uniformly formed in the longitudinal direction, but the male thread shape of the outer peripheral surface of the rotor 20 does not have to be uniform. By forming the inner peripheral surface of the stator 11 into a female thread shape that matches the male thread shape of the outer peripheral surface of the rotor 20, it is possible to configure the interference in the center of the conveying path to be thick and the interference at both ends to be thin.

[0026] As shown in Figure 2(b), when the rotor 20 is at the uppermost position, a transfer space 21a constituting a cavity of the first system with a maximum opening area is formed below the rotor 20 at the inlet portion, and liquid material is supplied from the supply pipe 7. When the rotor 20 rotates from the illustrated position, a transfer space 22a (see Figure 5 described below) constituting a cavity of the second system is dynamically formed above the rotor 20 at the inlet portion, and the opening area of ​​the transfer space 21a is reduced. As shown in Fig. 2(c), when the rotor 20 is at the uppermost position, a transfer space 21c constituting a cavity of the first system is formed below the rotor 20 at the position of line BB (see Fig. 5(a)). When the rotor 20 rotates from the illustrated position, the cross-sectional area of ​​the transfer space 21c below the rotor 20 decreases, and a transfer space 22c constituting a cavity of the second system is generated above the rotor 20, and the cross-sectional area of ​​the transfer space 22c further increases as the rotor 20 rotates (see Fig. 5(b) described below). As shown in FIG. 2(d), when the rotor 20 is in the uppermost position, transfer spaces 23 and 24 are formed on the left and right sides of the rotor 20 at the position of line CC. Here, the transfer space 23 communicates with the transfer spaces 21c and 22b to form a cavity of the first system, and the transfer space 24 communicates with the transfer spaces 21b and 22c to form a cavity of the second system (see FIG. 5 for the positions of the transfer spaces 21b, 21c, 22b, and 22c). When the rotor 20 rotates from the illustrated position, the cross-sectional area of ​​one of the transfer spaces 23 and 24 on the left and right sides of the rotor 20 decreases, while the cross-sectional area of ​​the other increases. For example, when the rotor 20 rotates from 0° to 90°, the transfer space 23 closes and the transfer space 24 reaches its maximum cross-sectional area.

[0027] As the rotor 20 rotates, two transfer spaces are repeatedly formed and closed at positions facing each other across the rotor 20 in each cross section (including the BB and CC cross sections) perpendicular to the flow path direction of the stator 11, causing the cavities filled with liquid material to move toward the outlet. The liquid material conveyed through the two transfer paths in the insertion hole 12 merges and is ejected from the nozzle member 13. To prevent pulsation of the liquid material conveyed through the two transfer paths, it is necessary to supply enough liquid material to fill each cavity in each transfer path and to ensure smooth confluence of the liquid material conveyed through the two transfer paths. To achieve these conditions, it is important to adjust the adhesion between the rotor 20 and the stator 11 at the inlet and outlet portions of the insertion hole 12.

[0028] (Adjusting the adhesion of the stator) The present invention solves the problem of pulsation by making the clamping force of the stator smaller at both ends than at the center where the rotor and stator contact. In other words, the problem of pulsation is solved by making the distribution of the adhesion force in the longitudinal direction of the rotor and stator smaller at both ends than at the center of the stator. The stator 11 is divided into three regions based on the adhesion force with the rotor 20. That is, the stator 11 is divided into a center portion where the adhesion force with the rotor 20 is constant, an inlet portion (region closer to the inlet than the center portion) where the adhesion force with the rotor 20 is smaller than at the center portion, and an outlet portion (region closer to the outlet than the center portion) where the adhesion force with the rotor 20 is smaller than at the center portion. In the example of Figure 3(b), B 13 and B 23 The part between is the center part, B 13 and B 11 The area between is the entrance, B 23 and B 21 The area between is the exit area. The adhesion of the stator can be adjusted by adjusting the shape of the stator (e.g., interference amount, thickness) and / or the material properties of the stator (e.g., repulsion force (rebound elasticity), hardness). In the first embodiment, the adhesion of the stator 11 consisting of the above three regions is achieved by adjusting the interference amount. That is, the adhesion is adjusted by making the interference amount smaller at both ends in the longitudinal direction of the stator 11 compared to the central portion, where the interference amount is constant, thereby solving the problem of pulsation. Below, a method for adjusting the adhesion of the stator 11 in the first embodiment will be described in detail with reference to FIGS. 2 to 4.

[0029] The portion of the stator 11 that the rotor 20 abuts is pressed by the rotor 20 to form an interference margin S 11 ,S 12 In Figure 2(a), the black painted area S 11 ,S 12 As can be seen from the figure, in the first embodiment, the stator 11 is arranged in close contact with the inner circumferential surface of the outer cylinder 10, and the interference margins S 11 ,S 12The longitudinal direction of the stator 11 is configured so that the amount of interference is smaller than that at the central portion in the longitudinal direction. Here, the longitudinal direction of the stator 11 is synonymous with the direction from the inlet to the outlet or from the outlet to the inlet, and is a direction perpendicular to the radial direction. The stator 11 includes a central portion 11c having a constant amount of interference, an inlet portion 11a having an interference amount that gradually (in steps) decreases from the central portion 11c toward the inlet (upstream), and an outlet portion 11b having an interference amount that gradually (in steps) decreases from the central portion 11c toward the outlet (downstream). The thickness of the inlet portion 11a and the outlet portion 11b of the stator 11 is configured to be thinner than that of the central portion 11c, thereby reducing the amount of interference, and therefore the adhesion force between the rotor 20 and the stator 11 is weaker than that at the central portion 11c. In the first embodiment, the quantitative ratio of interference between both ends of the stator 11 and the central portion in the longitudinal direction is, for example, both ends:central portion = 0.4 to 0.7: 1. The range (longitudinal length) of the inlet portion 11a and the outlet portion 11b of the stator 11 in the longitudinal direction is the same as the range (longitudinal length) of the inlet portion and the outlet portion of the insertion hole 12.

[0030] 3(a) is a side cross-sectional view of the outer cylinder 110, the stator 111, and the rotor 120 according to the prior art, and (b) is a side cross-sectional view of the outer cylinder 10, the stator 111, and the rotor 20 according to the first embodiment. 21 ,S 22 As can be seen from the figure, in the prior art, the diameter of the inner peripheral surface of the outer cylinder 110 in the longitudinal direction is constant, and the inner peripheral surface (female thread shape) of the stator 111 placed inside it is also formed uniformly in the longitudinal direction, and the male thread shape of the outer peripheral surface of the rotor 120 is also formed uniformly in the longitudinal direction. Therefore, the interference formed by the cooperation of the rotor 120 and the stator 11 is also constant. In other words, the interference S is formed over the entire longitudinal direction of the outer cylinder 110. 21 ,S 22 Therefore, in the conventional technology, there is a problem that pulsation is likely to occur when the liquid material that has passed through the two transport paths joins together. Furthermore, the conventional technology also has the problem of prone to pulsation due to insufficient supply of liquid material to the inlet of the stator 111. Specifically, there is a period of time during which the liquid material is not supplied to the transfer space while the rotor 120 moves within the interference range. For example, in a device in which the inlet opening of the stator 111 is closed by the interference when the rotor is at the 355° position, no liquid material is supplied during the rotation from 355° to 360° (and from 0° to 5°). The reduction in the amount of liquid material supplied by the rotation from 355° to 360° (and from 0° to 5°) leads to a reduction in the discharge amount due to the transport of the reduced liquid material, which causes pulsation.

[0031] On the other hand, in the first embodiment, the black border S in FIG. 3(b) is 11 ,S 12 As can be seen, the interference margins S near both ends of the outer cylinder 10 11 ,S 12 More specifically, the inner diameter of the outer cylinder 10 is constant along the longitudinal direction, but the inner peripheral surface (female thread shape) of the stator 11 disposed inside the outer cylinder 10 is smaller than the central portion of the insertion hole 12. 13 From the position of the inlet to the position B 11 Therefore, the amount of interference formed by the rotor 20 and the stator 11 working together decreases toward the inlet (B 13 >B 12 >B 11 Similarly, the inner peripheral surface (female thread shape) of the stator 11 is also at the outlet portion, and B 23 From the position of the outlet B 21 Therefore, the amount of interference formed in cooperation with the rotor 20 decreases toward the outlet (B 23 >B 22 >B 21). Therefore, the first embodiment can solve the problem that pulsation is likely to occur when liquid material that has passed through two transport paths joins together, and that pulsation is likely to occur when sufficient liquid material is not supplied to the inlet of the stator. For example, in the present invention, when the rotor is in the uppermost position at 360°, liquid material is supplied to the transport space (inlet of the transport path) at the inlet-side end until it reaches 358° (preferably until it reaches 359°, more preferably just before it reaches 360°). Similarly, liquid material is supplied to the transport space (inlet of the transport path) of the other system at the inlet-side end until it reaches 178° (preferably until it reaches 179°, more preferably just before it reaches 180°).

[0032] 4(a) is a cross-sectional view of the rotor 20 at the uppermost position (0°) in the inlet portion of the insertion hole 12, and FIG. 4(b) is a cross-sectional view of the rotor 20 at the uppermost position (0°) in the longitudinal central portion of the insertion hole 12. The travel distance (from S1 to opening position H1) required to open the inlet portion of the insertion hole 12 shown in FIG. 4(a) is shorter than the travel distance (from S2 to opening position H2) required to open the longitudinal central portion of the insertion hole 12 shown in FIG. 4(b), but the position of the upper end of the rotor 20 is the same. That is, the interference margin S1 (FIG. 4(a)) in the inlet portion of the insertion hole 12 is smaller by P1 than the interference margin S2 (FIG. 4(b)) in the central portion, so that the liquid material is easily supplied to the inlet of the transport path. From the viewpoint of quickly receiving a large amount of liquid material into the cavity, it is important to open the inlet of the transport path quickly (to shorten the time it is closed).

[0033] (Liquid material transport function) With reference to FIG. 5, the liquid material transport action caused by the rotation of the rotor 20 will be described. 5(a), when the rotor 20 is at the 0° position (uppermost position), a transfer space 21a forming a cavity appears at the most upstream side of the lower side of the rotor 20, and the transfer space 21a is filled with the liquid material supplied from the supply pipe 7. When the rotor 20 is at the 0° position, the transfer space above the rotor 20 is closed. As shown in FIG. 5(b), when the rotor 20 rotates to a 90° position, a transfer space 22a, which forms a cavity, appears at the uppermost upstream side of the rotor 20. Here, too, the uppermost upstream transfer space 22a is filled with liquid material supplied from the supply pipe 7. The transfer space 22b is connected to the transfer space 21a below the rotor 20 at the front side in the depth direction of the paper in the figure (to the left when viewed from the inlet side) to form a cavity (see transfer space 24 in FIG. 2(d)). As the cross-sectional area of ​​the transfer space 21a below the rotor 20 decreases, the liquid material present in the transfer space 21a moves toward the transfer space 22b. For the sake of explanation, the transfer spaces 21a and 22b, which form one cavity, are each assigned a different number. The same applies below. 5(c), when the rotor 20 rotates to the 180° position (lowest position), the transfer space 22a above the rotor 20 becomes fully open, as can be seen from the front cross-sectional view. On the other hand, the transfer space 21a below the rotor 20 becomes closed, and the liquid material present in the transfer space 21a moves toward the transfer space 22b. The transfer space 22a, which has become fully open, is filled with the liquid material supplied from the supply pipe 7.

[0034] As shown in FIG. 5(d), when the rotor 20 rotates to the 270° position, the cross-sectional area of ​​the transfer space 22a constituting the cavity on the upper side of the rotor 20 becomes smaller. The transfer space 22a is connected to the transfer space 21b on the lower side of the rotor 20 at the rear side in the depth direction of the paper in the figure (to the right when viewed from the inlet side) to form a cavity (see transfer space 23 in FIG. 2(d)). As the cross-sectional area of ​​the transfer space 22a decreases, the liquid material present in the transfer space 22a moves toward the transfer space 21b. Furthermore, as the cross-sectional area of ​​the transfer space 22b decreases, the liquid material present in the transfer space 22b moves toward the transfer space 21c. When the transfer space 21a reappears at the most upstream position on the lower side of the rotor 20, this transfer space 21a is filled with the liquid material supplied from the supply pipe 7. As shown in FIG. 5(e), when the rotor 20 rotates and reaches a 360° position, the transfer space 22a constituting the cavity on the upper side of the rotor 20 is closed. During this process, the liquid material present in the transfer space 22b moves toward the transfer space 21c, and the liquid material present in the transfer space 22a moves toward the transfer space 21b. When the transfer space 21a reappears at the most upstream position below the rotor 20, this transfer space 21a is filled with the liquid material supplied from the supply pipe 7. Here, the transfer spaces 21a, 21b, 21c, etc. that appear on the lower side of the rotor 20 constitute cavities that are separated from each other by the close contact between the rotor 20 and the stator 11. As described above, the rotor 20 repeatedly rotates from 0° to 360°, thereby transporting the liquid material from the inlet side to the outlet side within the insertion hole 12. When transporting the liquid material by rotating the rotor 20, it is important to fill the cavity with a sufficient amount of liquid material to prevent pulsation. In particular, it is preferable to reduce the adhesion force between the rotor 20 and the stator 11 when the rotor 20 is in the uppermost position (0°) and the lowermost position (180°).

[0035] (Relationship between interference amount and transfer space) The formation of the transfer space in a configuration with a small interference margin and a configuration with a large interference margin will be further explained with reference to Figs. FIG. 6 is a comparative diagram illustrating the formation of transfer spaces from 0° to 90° in a configuration in which the interference of the stator 11 is small (left diagram) and a configuration in which the interference is large (right diagram). As shown in FIG. 6(a), when the rotor 20 is at the uppermost position (0°), no transfer space is formed above the rotor 20 in either the configuration with small interference (left figure) or the configuration with large interference (right figure). 6(b), when the rotor 20 rotates and descends slightly from the uppermost position, in the configuration with a small interference margin (left diagram), a transfer space 22 is formed above the rotor 20. On the other hand, in the configuration with a large interference margin (right diagram), no transfer space 22 is formed above the rotor 20. 6(c), when the rotor 20 further rotates, even in the configuration with a large interference margin (right figure), a transfer space 22 is formed above the rotor 20. On the other hand, in the configuration with a small interference margin (left figure), a transfer space 22 with a larger cross section is formed above the rotor 20 than in the configuration with a large interference margin (right figure). As shown in Figure 6(d), when the rotor 20 rotates 90°, transfer spaces 21 and 22 with the same cross-sectional size are formed above and below the rotor 20 in both the configuration with a small interference (left figure) and the configuration with a large interference (right figure). 6, when the interference of the stator 11 is small, the close contact between the rotor 20 and the stator 11 is quickly released. In particular, when a configuration with a small interference is adopted for the outlet portion of the stator 11, the close contact between the rotor 20 and the stator 11 is quickly released, which is preferable because it allows the liquid material in the cavity formed in the transport path to quickly flow out.

[0036] FIG. 7 is a comparative diagram illustrating the formation of a transfer space from 270° to 360° in a configuration where the interference of the stator 11 is small (left diagram) and a configuration where the interference is large (right diagram). As shown in Figure 7(a), when the rotor 20 rotates 270°, transfer spaces 21 and 22 with the same cross-sectional size are formed above and below the rotor 20 in both the configuration with a small interference (left figure) and the configuration with a large interference (right figure). 7(b), when the rotor 20 is rotated slightly from 270°, the cross-sectional area of ​​the transfer space 22 above the rotor 20 is smaller even in the configuration with a large interference (right figure). On the other hand, in the configuration with a small interference (left figure), the transfer space 22 above the rotor 20 has a larger cross-sectional area than in the configuration with a large interference (right figure). 7(c), when the rotor 20 further rotates and approaches the uppermost position, the cross-sectional area of ​​the transfer space 22 above the rotor 20 becomes smaller in the configuration with a small interference (left diagram), but is not closed. On the other hand, in the configuration with a large interference (right diagram), the transfer space 22 above the rotor 20 is closed. As shown in FIG. 7(d), when the rotor 20 is at the uppermost position (360° (0°)), the transfer space above the rotor 20 is closed in both the configuration with small interference (left diagram) and the configuration with large interference (right diagram).

[0037] As can be seen from Figure 7, when the interference is large, the rotor 20 rotates and begins to contact the stator 11 earlier (see Figure 7(c)). Where the rotor 20 and stator 11 come into contact, the transfer space is closed and the liquid material is no longer filled into the stator 11 from the inlet. However, the rotor 20 continues to rotate until it reaches the maximum contact position (Figure 7(d)), continuing to expand the volume of the already closed cavity, which may result in the formation of a cavity that is not fully filled with liquid material. When a cavity that is not fully filled with liquid material at the outlet of the stator 11 opens to the nozzle member 13, the liquid material may be sucked in through the outlet of the nozzle member 13, which causes pulsation. In other words, by reducing the interference and always forming a cavity that is completely filled with liquid material, it is possible to eliminate pulsation.

[0038] (Range to make the interference smaller) A supplementary explanation will be given below regarding the range in which the interference is relatively small in the stator 11. Unless otherwise specified, the "range" described below refers to the range of the length of the stator 11 in the longitudinal direction. In the first embodiment, interference is provided over the entire length of the stator 11, and the range of the interference in the center portion of the stator 11 in the length direction is longer than the range of the interference in the inlet portion and the outlet portion of the stator 11 in the length direction. 13 ~B 23 The portion B is the central portion in the longitudinal direction of the conveying path formed in the insertion hole 12. 11 ~B 13 The portion B is an inlet portion of the conveying path formed in the insertion hole 12, 21 ~B 23 This portion is the outlet portion of the conveying path formed in the insertion hole 12.

[0039] Because the cavities in the two transfer paths described above move with a phase shift of 180° relative to the rotation of the rotor 20, if one wishes to consistently obtain the effect of reducing the interference in one of the two transfer paths, it is sufficient to reduce the interference in a range of one turn of the rotor 20 from both ends of the transfer path in the stator 11. If one wishes to consistently obtain the effect of reducing the interference in both transfer paths, it is necessary to reduce the interference in a range of one to two turns of the rotor 20 from both ends of the transfer path in the stator 11. The purpose of reducing the interference at the inlet portion of stator 11 is to ensure that the liquid material is sufficiently supplied to the inlet of the transport path. To achieve this purpose, it is preferable to reduce the interference in a range of at least one turn of rotor 20 from the inlet end of stator 11, preferably at least 1.2 turns of rotor 20 from the inlet end, and more preferably at least 1.5 turns of rotor 20 from the inlet end.

[0040] On the other hand, the purpose of reducing the interference at the outlet portion of the stator 11 is to allow the liquid material in the cavity to move smoothly to the nozzle member 13. To achieve this purpose, it is sufficient to always obtain the effect of reducing the interference in one of the two transport paths, so it is sufficient to reduce the interference in the range of one turn of the rotor 20 from the end of the stator 11 on the outlet side. By making the interference small in this range, it is possible to prevent pulsation. The effect of making the interference small is effective within the range where the rotor 20 and the stator 11 are in close contact with each other. For example, if there is a range (non-conveying action area) within the insertion hole 12 where the rotor 20 and the stator 11 are not always in contact with each other due to chamfering of parts, the effect is limited to the central range (conveying action area) excluding this range.

[0041] The minimum length of the rotor 20 in this device is two turns. To ensure reliable transport of the liquid material in the central portion of the transport path, it is preferable that the range of the central portion of the stator 11 in the longitudinal direction be two or more turns of the rotor. The total length of the stator 11 and the rotor 20 is preferably four or more turns, and considering the manufacturing tolerance of the elastic body, 4.5 or more turns is more preferable. From another perspective, it is preferable that the range of the central portion of the stator 11 in the longitudinal direction be longer than the ranges of both the inlet portion and the outlet portion of the stator 11. Therefore, to obtain the effects of the present invention, when the length (range) of the central portion of the stator 11 is shortest, the ratio of the inlet portion:the central portion:the outlet portion is 1:2:1, and the ratio of the central portion may be 2 or more. From the viewpoint that it is preferable that the range of the inlet portion is longer than the range of the outlet portion, when the length (range) of the central portion of the stator 11 is shortest, the ratio of the inlet portion:the central portion:the outlet portion is 3:5:2, and the ratio of the central portion may be 5 or more.

[0042] From another perspective, it is disclosed that the ratio of the range of the inlet portion in the longitudinal direction of stator 11 to the range of the central portion in the longitudinal direction is 3:5 to 10, and the ratio of the range of the outlet portion in the longitudinal direction of stator 11 to the range of the central portion in the longitudinal direction is 2:2 to 10. Here too, it is preferable to configure the range of the inlet portion in the longitudinal direction of stator 1 to be longer than the range of the outlet portion in the longitudinal direction of stator 1. In the first embodiment, the interference amount near both ends of the stator 11 is configured to decrease stepwise (in other words, gradually) toward both ends. Explaining the example of FIG. 3(b), if the inlet portion (or outlet portion) of the stator 11 is divided into three along the longitudinal direction, the inlet position B 11 (or outlet position B 21 ) has the smallest interference amount, followed by position B at the midpoint of the inlet 12 (or the midpoint of the outlet B 22) has a small interference amount. If such a change in interference amount is observed, it can be said that the interference amount is decreasing in stages. However, the concept of decreasing the interference amount in stages (in other words, gradually) of the present invention is not limited to the exemplified embodiment, and also includes an embodiment in which the interference amount at the inlet portion and outlet portion of stator 11 decreases steplessly or an embodiment in which the interference amount decreases non-uniformly in stages.

[0043] In the first embodiment described above, the interference margins S near both ends of the stator 11 11 ,S 12 The force at the ends of the stator 11 is smaller than that at the center, which reduces the adhesion force near both ends compared to the center of the stator 11, thereby solving the problem of pulsation. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to draw lines with a uniform line width on the surface of a workpiece. The relative movement device is configured, for example, with a known XYZ-axis servo motor and a ball screw, and can move the discharge port of the liquid material discharging device 1 to any position on the workpiece at any speed.

[0044] <Second embodiment> 8 is an explanatory diagram of the outer cylinder 210, stator 211, and rotor 220 according to the second embodiment, where (a) is a side cross-sectional view when the rotor 220 is at the uppermost position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder 210, and (f) is a rear view of the outer cylinder 210. Note that the second embodiment is similar to the first embodiment in terms of configuration other than the outer cylinder 210 and stator 211, and therefore description thereof will be omitted.

[0045] As shown in FIGS. 8(a) and 8(e), the outer cylinder 210 of this embodiment is configured such that its inner diameter gradually increases near both ends compared to its central portion. The outer cylinder 210 includes an inlet-side inner circumferential surface 210a that tapers toward the inlet, an outlet-side inner circumferential surface 210b that tapers toward the outlet, and a central inner circumferential surface 210c that defines a cylindrical space of constant diameter along the longitudinal direction. Thus, the outer cylinder 210 has a gradient on its inner circumferential surface that increases in diameter from the central portion toward the inlet and outlet, forming truncated cone-shaped spaces at the upstream and downstream ends. That is, the outer cylinder 210 of this second embodiment increases in diameter in a stepwise manner (i.e., gradually) at positions corresponding to the inlet and outlet portions of the insertion hole 212. The concept of increasing in diameter in a stepwise manner (i.e., gradually) is not limited to the stepless increase in diameter illustrated in FIG. 8, but also includes a non-uniform, stepwise decrease in diameter.

[0046] As shown in FIG. 8(c), when the rotor 220 is at the uppermost position, a transfer space 221c is formed below the rotor 220 at the position of line BB. When the rotor 220 rotates from the illustrated position, the cross-sectional area of ​​the transfer space 221c below the rotor 220 decreases, and a transfer space 222c (not shown) is formed above the rotor 220, and the cross-sectional area of ​​the transfer space 222c further increases as the rotor 220 rotates. As shown in FIG. 8(a), when the rotor 220 is at the uppermost position, a transfer space 221a with a maximum opening area is formed at the most upstream side below the rotor 220. When the rotor 220 rotates from the illustrated position, a transfer space 222a (not shown) that functions as an inlet of the transfer path is dynamically formed above the rotor 220, and the opening area of ​​the transfer space 221a decreases. As shown in FIG. 8(d), at the position of line CC, transfer spaces 223 and 224 are formed on the left and right sides of the rotor 220. Here, the transfer space 223 communicates with the transfer space 221c to form a cavity, and the transfer space 224 communicates with the transfer space 222c to form a cavity. When the rotor 220 rotates from the illustrated position, the cross-sectional area of ​​one of the transfer spaces 223 and 224 on the left and right sides of the rotor 220 decreases, while the cross-sectional area of ​​the other increases. For example, when the rotor 220 rotates from 0° to 90°, the transfer space 223 closes, and the transfer space 224 reaches its maximum cross-sectional area. In this way, when the rotor 220 rotates, at each cross section (including the BB cross section and the CC cross section) perpendicular to the flow path direction of the stator 211, two transport spaces are repeatedly formed and closed at positions opposite each other across the rotor 220, and the liquid material is transported through the insertion hole 212.

[0047] The stator 211 made of an elastic material is arranged in close contact with the inner peripheral surface (210a, 210b, 210c) of the outer cylinder 210. The stator 211 is fixed to the outer cylinder 210 so that the relative positions of the outer cylinder 210 and the stator 211 are not displaced due to the rotation of the rotor 220. For example, the outer cylinder 210 and the stator 211 are fixed by adhesive. The interference S drawn in black in FIG. 8(a) 211 ,S 212 As you can see, Shimeshiro S 211 ,S 212 Compared with the central portion 211c in the longitudinal direction of the stator 1, the amount of interference S between the inlet portion 211a and the outlet portion 211b is constant. 211 ,S 212 The amount of interference between the rotor 220 and the stator 211 gradually decreases. In addition, the inlet portion 211a and the outlet portion 211b of the stator 211 are configured to be thicker than the central portion 211c in the longitudinal direction, so the adhesion force between the rotor 220 and the stator 211 at the inlet and outlet portions is weaker than at the central portion. That is, in the second embodiment, the difference in adhesion force between the central portion of the stator 211 in the longitudinal direction and the inlet and outlet portions is greater than in the first embodiment. In this embodiment, the stator 211 has an inlet portion 211a and an outlet portion 211b whose radial thickness gradually (stepwise) increases toward the ends, so that the adhesion between the rotor 220 and the stator 211 gradually (stepwise) decreases toward the ends. However, the configuration in which the radial thickness at both ends of the outer cylinder 210 is thinner than that of the central portion is not limited to the second embodiment. For example, the outer cylinder 210 may be configured so that its radial thickness decreases by being rounded in a parabolic curve from the central portion toward the upstream end portion and the downstream end portion, or so that its radial thickness decreases in a stepped manner.

[0048] In the second embodiment described above, the interference margins S near both ends of the stator 211 (the inlet and outlet portions) are 211 ,S 212 The contact force between the rotor 220 and the stator 211 at the inlet and outlet portions of the insertion hole 212 is weaker than at the central portion, which makes it possible to solve the problem of pulsation. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to draw lines with a uniform line width on the surface of a workpiece. Furthermore, by making the inner diameter at both ends of the outer tube 210 larger than that at the central portion, the inlet portion 211a and the outlet portion 211b of the stator 211 smoothly expand in diameter, and the radial thickness gradually (in stages) increases toward the ends, so that the liquid material can be smoothly received into the inlet of the stator 211 and discharged from the outlet.

[0049] <Third embodiment> 9 is an explanatory diagram of an outer cylinder 310, a stator 311, and a rotor 320 according to the third embodiment, where (a) is a side cross-sectional view when the rotor 320 is at the uppermost position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder 310, and (f) is a rear view of the outer cylinder 310. Note that the configuration of the third embodiment is the same as that of the first embodiment except for the outer cylinder 310 and the stator 311, and therefore description thereof will be omitted.

[0050] 9(a) and 9(e), the outer cylinder 310 of this embodiment includes an inlet-side inner circumferential surface 310a that tapers toward the inlet, an outlet-side inner circumferential surface 310b that tapers toward the outlet, and a central inner circumferential surface 310c having an inner circumferential surface with an internal thread shape at the same pitch as the internal thread shape of the inner circumferential surface of the stator 311. The outer cylinder 310 is the same as the second embodiment in that truncated cone-shaped spaces are formed at the upstream end and downstream end, but differs in that the central inner circumferential surface 310c has an internal thread shape. The inner peripheral surface of the central portion of stator 311 has a female thread shape with the same pitch as rotor 320, and the outer peripheral surface of the central portion of stator 311 has a male thread shape with the same pitch as the inner peripheral surface. Stator 311, made of an elastic material, is arranged in close contact with the inner peripheral surface (310a, 310b, 310c) of outer cylinder 310. In the third embodiment, the central inner peripheral surface 310c of the outer cylinder is configured with an internal thread of the same pitch as the internal thread of the central inner peripheral surface of the stator 311. This allows the thickness of the central portion of the stator 311 to be uniform in the longitudinal direction, thereby enabling the adhesion force with the rotor 320 to be uniform in the central portion. When the stator 311 and the rotor 320 cooperate to form a conveying path, the trajectory of the rotor 320 is affected by a repulsive force generated when the stator 311 elastically deforms. However, this repulsive force is constant around the entire circumference of the contact surface with the rotor 320 within the range of the central inner peripheral surface 310c. Therefore, in the third embodiment, the trajectory of the rotor 320 is constant, resulting in a stable construction of the conveying path. In other words, in the third embodiment, the position of the rotor 320 is stable all around, resulting in a consistent cavity shape.

[0051] 9(b), when the rotor 320 is at the uppermost position, a transfer space 321a with a maximum opening area is formed at the most upstream side of the lower side of the rotor 320. When the rotor 320 rotates from the illustrated position, a transfer space 322a (not shown) is dynamically formed at the most upstream side of the upper side of the rotor 320, and the opening area of ​​the transfer space 321a is reduced. 9(c), at the position of line BB, a transfer space 321c is formed below the rotor 320. When the rotor 320 rotates from the position shown in the figure, the cross-sectional area of ​​the transfer space 321c below the rotor 320 decreases, and a transfer space 322c (not shown) is generated above the rotor 320, and the cross-sectional area of ​​the transfer space 322c further increases as the rotor 320 rotates. As shown in Figure 9(d), at the position of line CC, transfer spaces 323 and 324 are formed on the left and right sides of the rotor 320. Here, transfer space 323 communicates with transfer space 321c to form a cavity, and transfer space 324 communicates with transfer space 322c to form a cavity. When the rotor 320 rotates from the illustrated position, the cross-sectional area of ​​one of the transfer spaces 323 and 324 on the left and right sides of the rotor 320 decreases, while the cross-sectional area of ​​the other increases. For example, when the rotor 320 rotates from 0° to 90°, the transfer space 323 closes, and the transfer space 324 reaches its maximum cross-sectional area. In this way, when the rotor 320 rotates, at each cross section (including the BB cross section and the CC cross section) perpendicular to the flow path direction of the stator 311, two transport spaces are repeatedly formed and closed at positions opposite each other across the rotor 320, and the liquid material is transported through the insertion hole 312.

[0052] Also, the black outline S in Figure 9(a) 311 ,S 312 As can be seen from the amount of interference S in the inlet portion 311a and the outlet portion 311b compared to the central portion 311c of the stator 311, 311 ,S 312Therefore, even with the adjustment of the interference amount, the adhesion force between stator 311 and rotor 320 at the inlet and outlet portions is smaller than that at the center portion. 9(c) and 9(d), the central portion 311c of the stator 311 has a thinner radial thickness than the central portion 211c of the stator 211 of the second embodiment. Therefore, in the third embodiment, the difference in adhesion force between the longitudinal central portion of the stator 311 and the rotor 320 at the inlet and outlet portions is greater than in the second embodiment.

[0053] In the third embodiment described above, the adhesion force between the rotor 320 and the inlet and outlet portions of the stator 311 is weaker than that at the longitudinal center portion, so the problem of pulsation can be solved. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to draw lines with a uniform line width on the surface of a workpiece. Furthermore, compared to the second embodiment, it is possible to configure a larger difference in adhesion force between the longitudinal center portion of the stator 311 and the inlet and outlet portions.

[0054] <Fourth embodiment> 10 is an explanatory diagram of an outer cylinder 410, a stator 411, and a rotor 420 according to the fourth embodiment, where (a) is a side cross-sectional view when the rotor 420 is at the uppermost position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder 410, and (f) is a rear view of the outer cylinder 410. Note that the fourth embodiment is similar to the first embodiment in terms of configuration other than the outer cylinder 410 and the stator 411, and therefore description thereof will be omitted. 10(a) and 10(e), the outer cylinder 410 of this embodiment includes an inlet-side inner circumferential surface 410a that tapers toward the inlet, an outlet-side inner circumferential surface 410b that tapers toward the outlet, and a central inner circumferential surface 410c that has an inner circumferential surface with an internal thread shape that has substantially the same pitch as the internal thread shape on the inner circumferential surface of the stator 411. The outer cylinder 410 differs from the outer cylinder 310 of the third embodiment in that the internal thread shape on the central inner circumferential surface 410c has an edge, whereas the outer cylinder 310 of the third embodiment has a smooth internal thread shape without an edge.

[0055] The inner peripheral surface of the central portion of the stator 411 has a female thread shape with the same pitch as the rotor 420, and the outer peripheral surface of the central portion of the stator 411 has a male thread shape with an edge with substantially the same pitch as the inner peripheral surface. The stator 411 made of an elastic material is arranged in close contact with the inner peripheral surface (410a, 410b, 410c) of the outer cylinder 410. The interference margins S drawn in black in FIG. 10(a) 411 ,S 412 As you can see, Shimeshiro S 411 ,S 412 Compared with the central portion 411c of the stator 411 where the amount of interference is constant, the interference S 411 ,S 412 Therefore, even with the adjustment of the interference amount, the adhesion force between stator 411 and rotor 420 at the inlet and outlet portions is smaller than that at the center portion.

[0056] As shown in FIG. 10(b), when the rotor 420 is at the uppermost position, a transfer space 421a with a maximum opening area is formed at the most upstream side below the rotor 420. 10(c) and 10(d), the central portion 411c of the stator 411 is thinner in the radial direction than the central portion 211c of the stator 211 of the second embodiment. Therefore, the difference in adhesion force between the central portion of the stator 411 in the longitudinal direction and the rotor 420 at the inlet and outlet portions is greater than in the second embodiment.

[0057] In the fourth embodiment described above, the adhesion between the stator 411 and the rotor 420 is weaker at the inlet and outlet portions than at the center portion, so the problem of pulsation can be solved. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to draw lines of uniform width on the surface of a workpiece. In the fourth embodiment, there are fewer restrictions on forming the shape of the outer cylinder 410 by cutting compared to the outer cylinder 310 of the third embodiment, so manufacturing costs can be reduced.

[0058] <Fifth embodiment> 11 is an explanatory diagram of an outer cylinder 510, a stator 511, and a rotor 520 according to the fifth embodiment, in which (a) is a side cross-sectional view when the rotor 520 is at the uppermost position (0°), (b) is a rear view, (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), (e) is a side cross-sectional view of only the outer cylinder 510, and (f) is a rear view of the outer cylinder 510. Note that the configuration of the fifth embodiment is the same as that of the first embodiment except for the outer cylinder 510 and the stator 511, and therefore description thereof will be omitted.

[0059] 11(a) and 11(d), the outer cylinder 510 of this embodiment includes an upstream end portion inner circumferential surface 510a that defines a cylindrical space of constant diameter along the longitudinal direction, a downstream end portion inner circumferential surface 510b that defines a cylindrical space of constant diameter along the longitudinal direction, a central portion inner circumferential surface 510c that defines a cylindrical space of constant diameter along the longitudinal direction, an inlet-side tapered surface 510d, and an outlet-side tapered surface 510e. The inner circumferential surface of the stator 511 has a female thread shape with the same pitch as the rotor 520, and the outer circumferential surface of the stator 511 has the same shape as the inner circumferential surface of the outer cylinder 510. The stator 511, made of an elastic material, is disposed in close contact with the inner circumferential surface (510a to 510e) of the outer cylinder 510.

[0060] As shown in FIG. 11(b), when the rotor 520 is at the uppermost position, a transfer space 521a with a maximum opening area is formed at the most upstream side below the rotor 520. In the present embodiment, the upstream end portion inner circumferential surface 510a and the downstream end portion inner circumferential surface 510b of the outer cylinder 510 are formed into cylindrical shapes with larger diameters than the central portion inner circumferential surface 510c, which makes it possible to relatively weaken the adhesive force with the rotor 520 over a certain range from the inlet and outlet of the stator 511. Here, it is preferable that the upstream end portion inner circumferential surface 510a of the outer cylinder is formed over a length equivalent to one to two turns of the rotor 520 from the end of the stator 511 on the inlet side, and the downstream end portion inner circumferential surface 510b is formed over a length equivalent to one turn of the rotor 520 from the end of the stator 511 on the outlet side.

[0061] Furthermore, in the outer cylinder 510 of this embodiment, the longitudinal range (length) of the inner circumferential surface 510a of the upstream end portion is longer than the longitudinal range (length) of the inner circumferential surface 510b of the downstream end portion, thereby enabling smooth receipt of liquid material into the transfer path formed within the insertion hole 512. More specifically, the length of the inner circumferential surface 510a of the upstream end portion of the outer cylinder is preferably at least one turn of the rotor 520 from the end on the inlet side, and more preferably is configured so that the adhesion force can be weakened over a range of 1.5 turns of the rotor 520 so that the adhesion force can be sufficiently weakened without being affected by manufacturing tolerances, etc. Configuring the inlet portion of the transfer path formed within the insertion hole 512 to be relatively long is effective for sufficient receipt of liquid material and preventing pulsation. In the outer cylinder 510 of this embodiment, the radial thickness of the stator 511 gradually increases toward both ends due to the inlet-side tapered surface 510d, which increases in diameter toward the inlet, and the outlet-side tapered surface 510e, which increases in diameter toward the outlet. This also causes the adhesion between the rotor 520 and the stator 511 to gradually (in stages) weaken toward both ends. The inlet portion 511a of the stator 511 in the fifth embodiment corresponds to the inner circumferential surface 510a of the upstream end portion of the outer cylinder and the inlet-side tapered surface 510d. The outlet portion 511b of the stator 511 in the fifth embodiment corresponds to the inner circumferential surface 510b of the downstream end portion of the outer cylinder and the outlet-side tapered surface 510e, and is configured to be shorter than the inlet portion 511a of the stator 511. Pulsation can also be prevented in a mode, as in the fifth embodiment, in which the adhesion force of rotor 520 is gradually (stepwise) weakened at the boundary between the central portion of stator 511 and the inlet portion (or outlet portion), and the adhesion force of rotor 520 is constant at a position closer to the inlet (or outlet) than the boundary. That is, the technical idea of ​​gradually (stepwise) reducing the adhesion force of rotor 520 from the central portion of stator 511 in the longitudinal direction toward the outlet and inlet also includes a mode, as in the fifth embodiment, in which a tapered surface is provided on the inner peripheral surface of outer cylinder 510 that is not adjacent to the outlet or inlet.

[0062] In Figure 11(a), the black stripe S is drawn. 511 ,S 512 As you can see, Shimeshiro S 511 ,S 512 Compared with the central portion 511c of the stator 511 where the amount of interference is constant, the interference S 511 ,S 512 Therefore, the adhesion force between stator 511 and rotor 520 at the inlet and outlet portions of stator 511 is also reduced by adjusting the amount of interference.

[0063] In the fifth embodiment described above, the adhesion force between the stator 511 and the rotor 520 is weaker at the inlet and outlet portions than at the longitudinal center portion, thereby solving the pulsation problem. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to perform line drawing with a uniform line width on the surface of a workpiece. Furthermore, because the expanded diameter range of the inner circumferential surface of the outer cylinder 510 at the inlet portion is longer than in the second to fourth embodiments, the adhesion force at the inlet portion of the insertion hole 512 is weakened over a longer range, thereby enabling the liquid material to be more smoothly introduced into the transport path formed within the insertion hole 512. Thus, making the expanded diameter range of the inlet portion of the stator 511 longer than the outlet portion can be combined and applied to the third and fourth embodiments as well.

[0064] <Sixth embodiment> 12 is an explanatory diagram of an outer cylinder 610, a stator 611, and a rotor 620 according to the sixth embodiment, where (a) is a side cross-sectional view when the rotor 620 is at the uppermost position (0°), (b) is an AA cross-sectional view of (a), (c) is a BB cross-sectional view of (a), (d) is a CC cross-sectional view of (a), and (e) is a rear view omitting the rotor 620. Note that the sixth embodiment is similar to the first embodiment in terms of configuration other than the outer cylinder 610 and the stator 611, and therefore description thereof will be omitted.

[0065] 12(a), the outer cylinder 610 of this embodiment includes an upstream end portion inner circumferential surface 610a that defines a cylindrical space of constant diameter along the longitudinal direction, a downstream end portion inner circumferential surface 610b that defines a cylindrical space of constant diameter along the longitudinal direction, a central portion inner circumferential surface 610c that defines a cylindrical space of constant diameter along the longitudinal direction, an inlet-side tapered surface 610d, and an outlet-side tapered surface 610e. The inner circumferential surface of the stator 611 has a female thread shape with the same pitch as the rotor 620, and the outer circumferential surface of the stator 611 has the same shape as the inner circumferential surface of the outer cylinder 610. The stator 611, made of an elastic material, is disposed in close contact with the inner circumferential surface (610a to 610e) of the outer cylinder 610. In the present embodiment, the outer cylinder 610 has an upstream end inner peripheral surface 610a and a downstream end inner peripheral surface 610b formed into a cylindrical shape with a larger diameter than the central portion inner peripheral surface 610c, and therefore, it is possible to relatively weaken the adhesion force with the rotor 620 over a certain range from the inlet and outlet of the stator 611.

[0066] Furthermore, in the outer tube 610 of this embodiment, similar to the fifth embodiment, the longitudinal range (length) of the inner surface 610a of the upstream end portion of the outer tube is longer than the range (length) of the inner surface 610b of the downstream end portion, thereby enabling smooth acceptance of the liquid material into the conveying path formed within the insertion hole 612 and effectively preventing pulsation. In this embodiment, a receiving space 621a is provided adjacent to the inlet portion of the stator 611. The inner diameter of the receiving space 621a is large enough to prevent contact with the rotor 620 rotating in the receiving space 621a. In the receiving space 621a, the inner peripheral surface of the stator 611 does not always contact the rotor 620, so the receiving space 621a is a non-transport action area that does not have the effect of transporting the liquid material. That is, the insertion hole 612 of the stator 611 in this embodiment is divided into a transport action area and a non-transport action area. The boundary between the transport action area and the non-transport action area in the insertion hole 612 is the most upstream position where the rotor 620 contacts the stator 611, and is shown by reference numeral 612a in FIG. 12(a). The location shown by reference numeral 612a is the start position of the transport path, and this is the inlet of the transport path. The downstream side of reference symbol 612a constitutes a transport path that transports the liquid material. This transport path is a flow path that is created by inserting a rotor 620 having an externally threaded outer surface into the insertion hole 612. By eccentrically rotating the rotor 620 within the insertion hole 612, the cavities that are formed sequentially in the transport path move, and the liquid material that fills the cavities is transferred. The receiving space 621a is a space adjacent to the inlet of the transport path, and its diameter increases from the inlet of the transport path toward the upstream side.

[0067] 12(c), there is a gap between the inner peripheral surface of the stator 611 that defines the receiving space 621a and the outer peripheral surface of the rotor 620. From another perspective, the inner diameter of the insertion hole 612 of the stator 611 is configured to be largest at the end on the most upstream side. Furthermore, the receiving space 621a has a smaller volume than any of the cavities in the insertion hole 612 that are formed downstream of the receiving space 621a.

[0068] In this embodiment, the radial thickness of the stator 611 gradually increases toward the end due to the inlet-side tapered surface 610d of the outer cylinder, which increases in diameter toward the inlet, and the outlet-side tapered surface 610e, which increases in diameter toward the outlet, and this also causes the adhesion force between the rotor 620 and the stator 611 to gradually (in stages) weaken toward the end. Furthermore, in this embodiment, the adhesion force between the stator 611 and the rotor 620 is zero upstream of the inlet of the transfer path. In this embodiment, the inlet portion 611a of the stator 611 is a range corresponding to the inner peripheral surface 610a of the upstream end portion of the outer cylinder 610 and the inlet side tapered surface 610d of the transport action region, and does not include the non-transport action region. In this embodiment, the outlet portion 611b of the stator 611 is in a range corresponding to the inner circumferential surface 610b of the downstream end portion of the outer cylinder 610 and the outlet-side tapered surface 610e, and is configured to be shorter than the inlet portion 611a of the stator 611. The outlet portion 611b of the stator 611 in this embodiment does not have a non-conveying region, but when the stator is configured to include a non-conveying region, the outlet portion does not include this non-conveying region. In this embodiment, the length of the central portion 611c in the longitudinal direction of the stator 611 is at least twice the length of the inlet portion of the stator 611.

[0069] In the stator 611 of this embodiment, the amount of interference is constant in the central portion in the longitudinal direction, but the amount of interference gradually (in steps) decreases from the boundary with the central portion toward the boundary 612a with the receiving space. Furthermore, the amount of interference gradually (in steps) decreases from the boundary with the central portion in the longitudinal direction toward the outlet. The radial thicknesses of the inlet portion 611a and the outlet portion 611b of the stator 611 are also increased by the increased inner diameters of the inner circumferential surface 610a of the upstream end portion and the inner circumferential surface 610b of the downstream end portion of the outer cylinder 610. Therefore, the adhesive force at the inlet portion and the outlet portion of the insertion hole 612 is gradually (in steps) weakened. In addition, near the inlet of the insertion hole 612, a tapered surface that expands in diameter toward the upstream side is provided on the inner surface of the stator 611 to form a receiving space 621a, so that an amount of liquid material is supplied that always fills the cavity formed in the insertion hole 612.

[0070] In the sixth embodiment described above, the adhesion between the rotor 520 and the stator 511 is weaker at the inlet and outlet portions of the insertion hole 612 than at the central portion, and an enlarged receiving space 621a is provided near the inlet to allow the liquid material to flow smoothly, thereby solving the problem of pulsation. Therefore, by mounting the liquid material discharging device 1 of this embodiment on a coating device equipped with a relative movement device, it is possible to draw lines of uniform width on the surface of a workpiece. In this embodiment, a non-transport action area is provided only at the inlet portion of the insertion hole 612, but a non-transport action area may also be provided at the outlet portion of the insertion hole 612.

[0071] While the preferred embodiments of the present invention have been described above, the technical scope of the present invention is not limited to the above-described embodiments. Various modifications and improvements can be made without departing from the technical spirit of the present invention, and such modifications and improvements are also included within the technical scope of the present invention. For example, in the figures of the above-mentioned embodiments 1 to 6, the diameters of the inner peripheral surfaces of the upstream end portion and the downstream end portion of the outer cylinder are depicted as being the same size, but the technical scope of the present invention also includes embodiments in which the diameters of the inner peripheral surfaces of the upstream end portion and the downstream end portion of the outer cylinder are different, or embodiments in which the taper angles are different. Furthermore, in the above-described Embodiments 1 to 6, for example, the volume of the transfer space at the inlet portion and / or outlet portion of the insertion hole (12, 212, 312, 412, 512) may be configured to be larger than the volume of the transfer space at the longitudinal center portion of the insertion hole (12, 212, 312, 412, 512). With such a configuration, the liquid material that has moved through the transfer space in the insertion hole can be discharged as a flow with less pulsation.

[0072] Furthermore, in the above-described first to sixth embodiments, for example, the central portion of the rotor (20, 220, 320, 420, 520, 620) in the longitudinal direction may be configured to be thicker than the inlet and outlet portions. With such a configuration, even if the inner diameter of the insertion hole of the stator is the same from the inlet to the outlet, it is possible to make the adhesion force between the rotor and the stator at the inlet and outlet portions of the insertion hole smaller than the adhesion force between the rotor and the stator at the central portion of the insertion hole in the longitudinal direction. Furthermore, in the above-mentioned first to sixth embodiments, for example, the elastic force per unit volume of the central portion in the longitudinal direction of the stator may be configured to be greater than the elastic force per unit volume of the inlet portion and / or the outlet portion. As a specific example, it is disclosed that the elastic body in the central portion in the longitudinal direction of the stator is configured of an elastic body (e.g., rubber) with a higher density than the elastic body in the inlet portion and / or the outlet portion. Furthermore, the liquid material discharge devices of the first to sixth embodiments are not limited to applications for applying liquid materials, and can also be used as liquid feed pumps in circulation circuits, etc. By rotating the rotor in the opposite direction to that of the first to sixth embodiments, they can also be used as suction pumps.

[0073] The problems to be solved by the present invention can also be solved by combining the above-mentioned Embodiments 1 to 6. That is, it is possible to adopt the solution of any one of the above-mentioned Embodiments 1 to 6 at the inlet portion of the insertion hole (12, 212, 312, 412, 512, 612), and adopt the solution of any one of the above-mentioned Embodiments 1 to 5 at the outlet portion of the insertion hole (12, 212, 312, 412, 512, 612) that is different from the solution at the inlet portion. For example, the following combinations are also possible. (A) The inner diameter of the outer tube is gradually increased at the inlet portion (or outlet portion) of the insertion hole, thereby gradually increasing the radial thickness of the interference, and the amount of interference is gradually reduced while keeping the inner diameter of the outer tube constant at the outlet portion (or inlet portion) of the insertion hole, so that the adhesion force between the rotor and stator at the inlet and outlet portions of the insertion hole is smaller than the adhesion force between the rotor and stator at the longitudinal center portion of the insertion hole. (B) The inner diameter of the outer tube is gradually increased at the inlet (or outlet) portion of the insertion hole, thereby gradually increasing the radial thickness of the interference fit, and the inner diameter of the outer tube is kept constant at the outlet (or inlet) portion of the insertion hole, while the stator is made of a material with weaker elasticity than the central portion. (C) While the inner diameter of the outer tube is kept constant throughout its entire length, the amount of interference is gradually reduced at the outlet portion (or inlet portion) of the insertion hole, so that the adhesion force between the rotor and stator at the inlet and outlet portions of the insertion hole is smaller than the adhesion force between the rotor and stator at the center portion of the insertion hole in the longitudinal direction, and the stator is made of a material with weaker elasticity at the inlet portion (or outlet portion) of the insertion hole than at the center portion. (D) In ​​the above (A) to (C), a receiving space is provided in which the outer peripheral surface of the rotor located near the inlet of the insertion hole and the inner peripheral surface of the stator do not come into contact, and the diameter of the receiving space increases toward the inlet-side opening end of the insertion hole. [Explanation of symbols]

[0074] 1:Liquid material discharge device 2: Main unit 3: Rotor drive unit 10, 110, 210, 310, 410, 510: Outer cylinder 11,111,211,311,411,511: Stator 12, 112, 212, 312, 412, 512: Through holes 13: Nozzle member 14: Air vent hole 15: Stator unit 20, 120, 220, 320, 420, 520: Rotor 21, 121, 221, 321, 421, 521: (Under the rotor) Transfer space 22, 122, 222, 322, 422, 522: (Rotor) Transfer space 23, 123, 223, 323, 423, 523: (Rotor right) Transfer space 24, 124, 224, 324, 424, 524: (Left rotor) Transfer space

Claims

1. An outer cylinder and a stator having an insertion hole, which is a female-threaded through-hole, provided on the inner peripheral surface of the outer cylinder in close contact with the outer peripheral surface of the outer cylinder; a rotor having a male screw shape that is connected to a rotor drive unit and rotates eccentrically while contacting the inner circumferential surface of the stator, a fluid transfer device capable of transferring a fluid in a transfer path formed by the stator and the rotor by eccentrically rotating the rotor inserted into the insertion hole, the stator is configured to include an inlet portion occupying a certain range in the longitudinal direction from the inlet of the conveying path, an outlet portion occupying a certain range in the longitudinal direction from the outlet of the conveying path, and a central portion located between the inlet portion and the outlet portion, A fluid transfer device characterized in that the adhesion force exerted by the rotor at the inlet portion and the outlet portion of the stator is smaller than the adhesion force exerted by the rotor at the central portion.

2. 2. The fluid transfer device according to claim 1, wherein the central portion has a uniform contact force exerted by the rotor along the longitudinal direction.

3. (A) When the adhesion force between the rotor and the stator at the inlet of the conveying path is A1, the adhesion force between the rotor and the stator at a position one turn of the rotor from the inlet of the conveying path is A2, the adhesion force between the rotor and the stator at a position between the inlet of the conveying path and the position one turn of the rotor from the inlet of the conveying path is A3, and the adhesion force between the rotor and the stator at the center part in the longitudinal direction of the conveying path is A4, the relationship A4>A2>A3>A1 is satisfied; and / or (B) A fluid transfer device as described in claim 2, characterized in that when the adhesion force between the rotor and the stator at the outlet of the conveying path is B1, the adhesion force between the rotor and the stator at a position one turn of the rotor from the outlet of the conveying path is B2, the adhesion force between the rotor and the stator at a position between the outlet of the conveying path and a position one turn of the rotor from the outlet of the conveying path is B3, and the adhesion force between the rotor and the stator at the longitudinal center portion of the conveying path is B4, the relationship is B4>B2>B3>B1.

4. 2. The fluid transfer device according to claim 1, wherein the amount of interference caused by the rotor is uniform across the longitudinal center portion of the insertion hole.

5. (A) When the interference amount between the rotor and the stator at the inlet of the conveying path is A1, the interference amount between the rotor and the stator at a position one turn of the rotor from the inlet of the conveying path is A2, the interference amount between the rotor and the stator at a position between the inlet of the conveying path and the position one turn of the rotor from the inlet of the conveying path is A3, and the interference amount between the rotor and the stator at the center portion in the longitudinal direction of the conveying path is A4, a relationship of A4>A2>A3>A1 is satisfied; and / or (B) A fluid transfer device according to claim 4, wherein the relationship is B4>B2>B3>B1, where the interference amount between the rotor and the stator at the outlet of the conveying path is B1, the interference amount between the rotor and the stator at a position one turn of the rotor from the outlet of the conveying path is B2, the interference amount between the rotor and the stator at a position between the outlet of the conveying path and the position one turn of the rotor from the outlet of the conveying path is B3, and the interference amount between the rotor and the stator at the center portion of the longitudinal direction of the conveying path is B4.

6. 6. The fluid transfer device according to claim 2, wherein the central portion of the insertion hole in the longitudinal direction extends over an area corresponding to at least two turns of the rotor.

7. The inlet portion is in a range from the inlet of the conveying path to more than one turn of the rotor, 7. The fluid transfer device according to claim 2, wherein the outlet portion is in a range from the outlet of the transport path to more than one turn of the rotor.

8. 8. The fluid transfer device according to claim 2, wherein the longitudinal extent of the central portion of the stator is longer than the longitudinal extents of the inlet portion and the outlet portion.

9. 9. The fluid transfer device according to claim 2, wherein a ratio of an interference amount by the rotor at the inlet portion and the outlet portion of the stator to an interference amount by the rotor at the central portion of the stator is 0.4 to 0.7:

1.

10. A fluid transfer device as described in any one of claims 2 to 9, characterized in that the shape and / or material properties of the stator at the inlet portion and the outlet portion are set to specifications different from those of the central portion so that the adhesion force between the stator and the rotor at the inlet portion and the outlet portion is smaller than the adhesion force between the stator and the rotor at the central portion of the stator.

11. at the inlet portion of the conveying path, one of the material characteristics and thickness of the stator, as well as the interference amount of the stator, is set to a specification different from that of the central portion of the insertion hole, so that the adhesion force between the stator and the rotor at the inlet portion of the conveying path is smaller than the adhesion force between the stator and the rotor at the central portion of the stator, 10. A fluid transfer device according to claim 2, wherein at the outlet portion of the transport path, the amount of interference of the stator as well as any one of the material properties and thickness of the stator are set to specifications different from those of the central portion of the insertion hole, so that the adhesion force between the stator and the rotor at the outlet portion of the transport path is smaller than the adhesion force between the stator and the rotor at the central portion of the stator.

12. A fluid transfer device as described in any one of claims 2 to 9, characterized in that the longitudinal central portion of the stator is made of a material having a stronger elastic force than the material constituting the inlet portion and / or outlet portion of the stator.

13. 13. The fluid transfer device according to claim 2, wherein the inner circumferential surface of the outer cylinder at the upstream end portion and the downstream end portion has a larger diameter than the central portion of the outer cylinder in the longitudinal direction.

14. 14. The fluid transfer device according to claim 13, wherein a central portion in the longitudinal direction of the outer cylinder has an inner circumferential surface with the same diameter.

15. 14. The fluid transfer device according to claim 13, wherein a central portion of the outer cylinder in the longitudinal direction has an inner peripheral surface having a female thread shape with the same pitch as that of the stator.

16. 16. The fluid transfer device according to claim 15, wherein an uneven shape is formed on the outer peripheral surface of the outer cylinder at a position corresponding to the inner peripheral surface of the female thread shape.

17. A fluid transfer device as described in any one of claims 13 to 16, characterized in that the inner circumferential surface at the upstream end portion of the outer cylinder is configured as a tapered surface whose diameter increases toward the upstream end of the outer cylinder, and the inner circumferential surface at the downstream end portion of the outer cylinder is configured as a tapered surface whose diameter increases toward the downstream end of the outer cylinder.

18. 18. A fluid transfer device as described in any one of claims 13 to 17, characterized in that the outer cylinder comprises an upstream end portion inner peripheral surface having an inner peripheral surface of the same diameter, an inlet side tapered surface connecting the upstream end portion inner peripheral surface and the central portion, a downstream end portion inner peripheral surface having an inner peripheral surface of the same diameter, and an outlet side tapered surface connecting the downstream end portion inner peripheral surface and the central portion.

19. A fluid transfer device as described in any one of claims 13 to 18, characterized in that the range of the expanded inner circumferential surface at the upstream end portion of the outer cylinder is longer than the range of the expanded inner circumferential surface at the downstream end portion of the outer cylinder.

20. A fluid transfer device as described in any one of claims 1 to 19, characterized in that the ratio of the longitudinal range of the inlet portion of the stator to the longitudinal range of the central portion of the stator is 3:5 to 10, and the ratio of the longitudinal range of the outlet portion of the stator to the longitudinal range of the central portion of the stator is 2:5 to 10.

21. A fluid transfer device as described in any one of claims 1 to 20, characterized in that the stator is composed of a transport action area having an interference with the rotor and a non-transport action area located upstream of the transport action area and not in contact with the rotor (having no interference).

22. A fluid transfer device as described in claim 21, characterized in that the inner surface of the insertion hole that constitutes the non-transporting action area is configured as a tapered surface that expands in diameter from the center side of the insertion hole toward the inlet side.

23. A fluid transfer device as described in claim 21 or 22, characterized in that the volume of the non-transport action area is smaller than the volume of any of the transport spaces within the insertion hole located in the transport action area and opened and closed by eccentric rotation of the rotor.

24. A fluid transfer device as described in any one of claims 1 to 23, characterized in that the adhesion force between the stator and the rotor at the inlet and / or outlet portions is weakest when the rotor is in the uppermost and lowermost positions.

25. 25. The fluid transfer device according to claim 1, further comprising a nozzle member having a discharge port for discharging the fluid flowing out from the outlet of the transport path.

26. A fluid transfer device described in any one of claims 1 to 25, characterized in that the stator is fixed to the outer cylinder so that its relative position with the outer cylinder does not shift due to the rotational movement of the rotor.

27. ​​A fluid transfer device as described in Claim 26, characterized in that the outer tube and the stator are adhesively fixed together.

28. A fluid transfer device according to any one of claims 1 to 27; a relative movement device that moves the fluid transfer device and the object to be coated relatively.

29. A coating method for drawing a line having a uniform line width on a surface of a workpiece, using the coating device according to claim 28.

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