JPH0217121Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a positive displacement fluid machine generally referred to as a C-ring pump or scroll pump.

As this type of fluid machine, for example, the above-mentioned C
Ring-type pumps are known, but in the case of this C-ring type pump, a C-shaped groove is provided on the end face of the case, one end communicating with the inlet and the other end communicating with the outlet. A disk that fits loosely between the inner surfaces of the C-shaped groove from a disk that is attached to the open end surface of the groove, and whose tip surface slides into contact with the bottom surface of the C-shaped groove.
A protruding C-shaped wing is provided at a predetermined distance from the center of curvature of the C-shaped groove so that at least one of the inner circumferential surface and the outer circumferential surface of the C-shaped wing abuts the inner surface of the C-shaped groove. The fluid filling the C-shaped groove is moved from the inlet side to the outlet side by making the C-shaped blade perform a sliding motion along its eccentric trajectory. and a pump unit configured to obtain. The following explanation will focus on such a C-ring type pump, but according to a fluid machine with such a configuration, a plurality of pump units are connected in series, and the C-shaped blades of these units are mutually connected at a required angle. By allowing the units to operate synchronously with different phases, it is possible to construct a positive displacement pump with no pulsation, and conversely, it is possible to construct a positive displacement pump with no pulsation. By forcibly operating the C-shaped blades of each of these units and extracting the operating force to the outside, it is possible to use flowmeters with low pressure loss and a wide range of applications from high speed to low speed. It is possible to construct a motor that operates stably.

However, in such a configuration, the above C
Unless the seal between the bottom surface of the groove and the tip of the C-shaped blade or the seal between the open end surface of the C-shaped groove and the disk is properly performed, the performance cannot be fully exhibited. Therefore, in such a fluid machine, it is not only possible to adjust the contact pressure of the seal portion described above, but also it is important that the adjusted contact pressure is stably maintained at a constant value during operation. In addition, it is desirable to take measures to prevent a situation in which the contact pressure decreases and the sealing performance deteriorates even if the seal portion becomes abraded after long-term use.

In order to meet these demands, for example,
As shown in Japanese Patent No. 52-57507, there is a sealing member which is movably held on the case side and slidably contacts the tip of the disk or wing. However, this method requires a plurality of types of seal members to be brought into elastic contact with the corresponding disks and blades using different springs, so there are problems in that the number of parts increases and assembly is time-consuming.

In addition, as another measure, a relatively strong spring can be used to press the entire disk in the direction of the groove, so that the disk can be sealed with the open end surface of the groove, and the tip of the blade can be sealed with the bottom surface of the groove at the same time. It is also possible. However, since such a spring is relatively bulky, there is a problem in that it prevents the device from being made more compact.

In this type of fluid machine, the inner surface of the C-shaped groove is made into a tapered surface, and the outer peripheral surface or the inner peripheral surface of the blade whose tip side is thinner than the base end side is brought into line contact with the tapered surface. There is something I did. However, with such a configuration, a gap is likely to occur between the tip of the blade and the bottom surface of the groove due to the blade coming off and moving in the radial direction along the tapered surface. To prevent this, it is possible to press the disk from the back side with a strong spring, but if the pressing force is too large, the sliding friction between the blade and the groove will increase, increasing power loss and causing wear. A problem arises in that durability is reduced.

The present invention aims to eliminate all such inconveniences.

In order to achieve the above object, the present invention provides a positive displacement fluid machine as described above, in which backing members are disposed opposite to each other on the back surface of the disk, and
A guide pin for causing the C-shaped or spiral-shaped blade to perform a sliding motion while being guided by the cam surface is made into a cylindrical body, and is protruded from a portion corresponding to the C-shaped or spiral-shaped blade on the back surface of the disk. , a spring member is housed inside the guide pin for pressing the disc against the backing member in a C-shaped or spiral groove direction.

In particular, in the present invention, the guide pin is not only cylindrical, but also guided by a cam surface in a line contact state, thereby causing the disk to move more radially than necessary. The disk is made to perform an accurate grinding motion by regulating the movement of the disk.

Hereinafter, an embodiment in which the present invention is applied to a C-ring type pump will be described with reference to the drawings.

A first pump unit A and a second pump unit B are connected in series. Each pump unit A, B has C-shaped grooves 3, 4 opened in one end surface 1a, 2a of the cases 1, 2, and is connected to a disk 5, 6 with a lid attached to the open end surface of the C-shaped groove 3, 4. A C that fits loosely between the inner surfaces 7 and 8 and 9 and 10 of the C-shaped grooves 3 and 4, and whose tip surfaces 11 and 12 slide in liquid-tight contact with the bottom surfaces 13 and 14 of the C-shaped grooves 3 and 4. C-shaped wings 15, 16 are integrally provided, and the C-shaped wings 15, 16 are integrally provided.
16, the outer peripheral surfaces 17, 18 of the C-shaped blades 15, 16
and are arranged eccentrically by a predetermined distance from the center of curvature 0 of the C-shaped grooves 3, 4 so that at least one of the inner circumferential surfaces 19, 20 abuts the inner surfaces 7, 8, 9, 10 of the C-shaped grooves. , the C-shaped blades 15 and 16 are caused to perform orbital circular motion along their eccentric orbits. The C-shaped grooves 3 and 4 are each 3/4+
It has an α-arc shape, and has one end communicating with the inflow ports 21 and 22, and the other end communicating with the outflow ports 23 and 24. The outflow port 23 of the first pump unit A is connected to the inflow port 22 of the second pump unit B. Further, the C-shaped blade 15,
Reference numeral 16 has a 3/4+α arc shape, and the radius of curvature of the inner surfaces 7 and 9 on the outside of the C-shaped grooves 3 and 4 at a predetermined depth position is r ₁ , and The radius of curvature of the side surfaces 8 and 10 is r ₂ , and the C-shaped blades 15 and 16
If the average radius of curvature of is R, then R=r ₁ + r ₂ )/
The shape and dimensions are set such that two relational expressions are satisfied. Then, C of the first pump unit A
C-shaped vanes 15 and C-shaped vanes 16 of the second pump unit B
The two are made to move synchronously with a phase difference of 90 degrees from each other. In addition,
The inner surfaces 7, 8, 9, 10 of these C-shaped grooves 3, 4 are
As clearly shown in FIG. 1, the blades 15, 16 have tapered surfaces that widen toward the open end, and are in line contact with the inner surfaces 7, 8, 9, 10.
has a cross-sectional shape in which the distal end is thinner than the proximal end. Here, the scouring motion of the C-shaped blades 15, 16 refers to a state in which each part of the C-shaped blades 15, 16 simultaneously moves to draw a full circle with the same diameter D, and the diameter D is It corresponds to the value obtained by subtracting the width dimension W of the C-shaped blades 15 and 16 from the width dimension (r ₂ −r ₁ ) of the C-shaped grooves 3 and 4 at a predetermined cross-sectional position.
In this embodiment, the pump units A and B are arranged back to back with their axes aligned, and the blade actuating mechanisms 27 and 28 share a rotating shaft 26 inserted through the axes of the pump units A and B. Each of the C-shaped blades 15,
Each of the 16 students is asked to perform the Misosuri exercise. The blade operating mechanisms 27 and 28 are connected to the rotating shaft 2.
6, and a bearing 2 mounted on the outer periphery of the rotating shaft 26 so as to be slidable in a direction in which the amount of eccentricity increases or decreases.
The shaft holes 3 of the disks 5 and 6 are connected through the holes 9 and 30.
Eccentric cam 3 rotatably engaged with the inner periphery of 1 and 32
3, 34, and spring members 35, 36, which urge the eccentric cams 33, 34 in the direction of increasing the amount of eccentricity. Specifically, flat surface portions 37 and 38 are formed parallel to the outer circumferential surface of the rotating shaft 26, and radial grooves 39 and 40 are provided in the cylindrical eccentric cams 33 and 34. The flat surface portions 37 and 38 of the rotating shaft 26 are slidably fitted in the radial direction. Further, spring holding holes 41..., 42... are provided at the terminal ends of the grooves 39, 40 of the eccentric cams 33, 34, and the spring members 3 are accommodated in the spring holding holes 41..., 42...
5..., 36, the eccentric cams 33, 34
is biased in a direction that increases the amount of eccentricity of the eccentric cams 33, 34 with respect to the rotating shaft 26. That is, the spring members 35..., 36
The C-shaped blades 15, 16 are pressed against the inner surfaces 7, 8, 9, 10 of the C-shaped grooves 3, 4 by the urging force of the C-shaped grooves 3, 4. Further, a guide plate 43 is disposed between the disks 5 and 6 of the pump units A and B. The guide plate 43 is disk-shaped and has a thick wall portion 43a at its peripheral edge, and the thick wall portion 43a is sandwiched and fixed between the cases 1 and 2.
In this guide plate 43, which is a member on the case 1, 2 side, a plurality of guide parts 44 having circular cam surfaces 44a on the inner periphery are bored at equiangular intervals in the circumferential direction. , engages in line contact with the cam surface 44a forming the cylindrical surface of each guide portion 44 on the side of the disks 5, 6.
A guide pin 45 is provided to prevent the C-shaped blades 15 and 16 from rotating relative to the cases 1 and 2 and to cause the C-shaped blades 15 and 16 to perform a sliding motion. Each guide pin 45 has a cylindrical shape, and has one end supported on the back surface of one disk 5 so as to be able to slide a certain amount in the axial direction, and the other end supported on the back surface of the other disk 6 axially. It is supported so that it can slide a certain amount in the direction of the heart. That is, one disk 5
When paying attention to this, as clearly shown in FIG. 1, a guide pin 45 is provided protrudingly at a portion corresponding to the C-shaped blade 15 on the back surface of the disk 5.
Focusing on the other disk 6, a guide pin 45 is provided protruding from a portion of the back surface of this disk 6 that corresponds to the C-shaped wing 16. The guide portions 44 . The dimensions of the guide pins 45 are set. In addition, each of the disks 5 and 6
A backing member is disposed opposite to each other on the back surface of the disc, and a spring member 46 is interposed between the backing member and the discs 5, 6 to press the discs 5, 6 in the direction of the corresponding C-shaped grooves 3, 4. are doing. Specifically, a spring member 46 for urging the disks 5 and 6 away from each other is housed inside the guide pin 45, and one disk 5 is used as a backing member for the other disk 6. In addition, the other disk 6 is made to play the role of a backing member for one disk 5.

If it has such a configuration, the C-shaped blade 15,
The outer peripheral surfaces 17 and 18 of 16 are C at the outer contact part.
In line contact with the outer inner surfaces 7, 9 of the C-shaped grooves 3, 4, the inner circumferential surfaces 19, 20 of the C-shaped wings 15, 16 are in line contact with the inner inner surfaces 8, 9 of the C-shaped grooves 3, 4 at the inner contact portions. 10, the inside of the C-shaped grooves 3, 4 is formed into sickle-shaped spaces 3a, 4a on the inlet side and space 3 on the outlet side by the C-shaped blades 15, 16.
It is divided into 4b and 4b. From this state, when the rotating shaft 26 is rotated in the direction of the arrow X to cause the C-shaped blades 15 and 16 to perform a sliding motion, the outer contact portion and the inner contact portion are moved into the C-shaped grooves 3 and 16, respectively. Since it moves along the inner surfaces 7, 8, 9, and 10 from the inlet ports 21, 22 side to the outlet ports 23, 24 side, both spaces 3a, 3b, 4a, and 4b also move in the same direction. , these both spaces 3a, 3
The fluid filling b, 4a, 4b flows into the inlet 2
It will be conveyed from the 1, 22 side to the outlet 23, 24 side. In addition, in the process of the C-shaped blades 15 and 16 performing a sliding motion, there is a period when the external contact portion temporarily disappears (see the first pump unit A in FIG. 4) and a period when the internal contact portion temporarily disappears. The period when the pump runs out (see the second pump unit B in FIG. 3) occurs periodically. Each of the C-shaped blades 1 is arranged so that the timings of the first pump unit A and the second pump unit B do not overlap.
Since the phases of the scraping motions 5 and 16 are different, the inlet 21 of the first pump unit A and the outlet 24 of the second pump unit B are connected through the C-shaped grooves 3 and 4 without resistance. A situation where communication occurs in this state cannot occur even for a moment. Therefore, with such a structure, the fluid sucked from the inlet 21 passes through both the C-shaped grooves 3 and 4 in sequence and is reliably guided to the outlet 24 from the outlet 24. The pump action of subsequent discharge can be performed without using any valves or the like.

This kind of operation is obtained because, in this fluid machine, each disk 5, 6 is pressed in the direction of the corresponding C-shaped groove 3, 4 by the urging force of the spring member 46. By selecting the strength of these spring members 46..., the bottom surfaces 13, 14 of the C-shaped grooves 3, 4 and the C
The contact pressure of the seal portion existing between the tip surfaces 11, 12 of the shaped blades 15, 16, or the seal portion existing between the open end surfaces of the C-shaped grooves 3, 4 and the disks 5, 6. It can be adjusted as appropriate. Further, since this contact pressure is obtained by the elastic force of the spring members 46,
It is possible to maintain this value stably during operation, and furthermore, even if the seal portion is worn to some extent, the contact pressure does not change significantly.

In this case, the portions corresponding to the C-shaped wings 15, 16 on the back surfaces of the disks 5, 6 are pressed by the spring member 46, so that each portion can be sealed evenly. That is, if other parts are pressed by the spring member 46, there is a risk that the disks 5, 6 themselves will warp slightly using the C-shaped blades 15, 16 as fulcrums. Therefore, disks 5 and 6
Either the sealing performance between the C-shaped blades 15, 16 and the bottom surfaces 13, 14 of the C-shaped grooves 3, 4 is degraded. In contrast, the device of the present invention uses the spring member 46 to press the portion that becomes the fulcrum of warping, so there is no risk of warping of the disks 5 and 6 even when pressed with strong force, and each part Sealing performance can be maintained at a high value. Further, since the guide pin 45 for performing the miso grinding motion is made into a cylindrical body, and the spring members 46 are respectively housed inside the guide pin 45,
There is no need to secure a special space for arranging the spring member 46. Therefore, the entire fluid machine can be made more compact.

Moreover, in this case, the outer periphery of the guide pin 45 that holds the spring member 46 is guided by the cam surface 44 in a line contact state.
Wings 15, 1 along the inner surfaces 7, 8, 9, 10 of 4
6 is reliably prevented from coming off and moving in the radial direction.
That is, the cam surface 44a is
Since the dimensions are set to correspond to the scraping motion of 6, the C-shaped blades 15, 16 are
The movement of moving in the radial direction while coming out of the grooves 3 and 4 along the cam surfaces 44a
The guide pin 45 is regulated by line contact with the guide pin 45. Therefore, it is possible to effectively prevent the tips 11 of the C-shaped grooves 3, 4 from separating from the bottom surfaces 13 of the grooves 3, 4, even if they are not pressed into the C-shaped grooves 3, 4 with a strong spring. can. Therefore, it is possible to use a relatively low-force and compact spring member 46, and from this point of view as well, it is possible to achieve a reduction in size and weight. By reducing frictional resistance as much as possible, it is possible to reduce power loss and improve durability.

Note that the above embodiments are for the case where the fluid machine according to the present invention is used as a pump, but conversely, if the fluid is made to flow through each of the above units, this fluid machine can be used as a flow meter or a motor. It is something that can be used.

Further, in the above embodiment, a case was explained in which two sets of units were connected in series, but the present invention includes a case having only one set of units, a case having three sets of units, and a case having three sets of units.
It also includes units equipped with more than one set.

Furthermore, it goes without saying that the backing member is not limited to those mentioned above; for example, when a fluid machine is configured as a single unit, a special backing member fixed to the case may be used to support the disk. Must be placed on the back. In this case, at least one end of the spring member must be brought into sliding contact with the backing member.

Further, as described above, the present invention can also be applied to a spiral pump (scroll pump) or a motor equipped with a unit consisting of a combination of spiral blades and grooves. An example of this spiral fluid machine is shown in Japanese Patent Application Laid-open No. 104609/1983 entitled "Compressor for Compressible Media."

Since the present invention has the above configuration, the seal portion existing between the bottom surface of the C-shaped or spiral groove and the tip surface of the C-shaped or spiral blade, and the opening end surface of the C-shaped or spiral groove and the disk. Not only is it possible to adjust the contact pressure at the sealing part that exists between the This makes it possible to provide a positive displacement fluid machine that does not cause inconveniences such as a decrease in contact pressure and deterioration of sealing performance even if parts are worn.

In particular, this product seals all parts at the same time by pressing the disk with a spring member, so not only is the structure simple with fewer parts, but the position where the spring member presses the disk has been devised. This prevents the inconvenience of partial deterioration of sealing performance due to warpage of the disk. Moreover, since the spring member is housed inside the existing guide pin, it is possible to achieve the effect of easily achieving compactness.

Furthermore, since the guide pin is brought into line contact with the cam surface to ensure the trajectory of the blade's scraping motion and prevent the blade from moving outside the trajectory, the inner surface of the groove is tapered. Despite this, there is no need to use a strong spring to press the blade into the groove, which reduces power loss, reduces wear, and improves durability.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, in which FIG. 1 is a front sectional view, FIG. 2 is a sectional view taken along the line - in FIG. 1,
FIG. 3 is a partial side sectional view, and FIGS. 4 and 5 are diagrams explaining the principle. A, B...Unit, 1, 2...Case, 3,
4... C-shaped groove, 5, 6... Disc (backing member),
7, 8, 9, 10...inner surface, 15, 16...C
Shaped blades, 17, 18...inner circumferential surface, 19, 20... outer circumferential surface, 21, 22... inlet, 23, 24... outlet, 45... guide pin, 46... spring member.

Claims (1)

[Claims for Utility Model Registration] (1) A C-shaped or spiral groove is provided on the end surface of the case, one end communicating with the inlet and the other end communicating with the outlet, and the opening of this C-shaped or spiral groove. A C-shaped or spiral wing that fits loosely between the tapered inner surfaces of the C-shaped or spiral groove from a disk capped on the end surface, and whose tip surface is in close contact with the bottom surface of the C-shaped or spiral groove. and the C-shaped or spiral-shaped blade is arranged so that at least one of the inner peripheral surface and the outer peripheral surface of the C-shaped or spiral-shaped blade is in line contact with the inner surface of the C-shaped or spiral groove. In the C-shaped or spiral-shaped groove, by placing the blade eccentrically by a predetermined distance from the center of curvature of the C-shaped or spiral-shaped groove, and causing the C-shaped or spiral-shaped blade to perform a writhing motion along its eccentric trajectory. A positive displacement fluid machine comprising a unit configured to move fluid filling the disk from the inflow port side to the outflow port side, wherein a backing member is disposed opposite to the back surface of the disk, and , the guide pin is guided in line contact with the cam surface to cause the C-shaped or spiral-shaped blade to perform a sliding motion, and the guide pin is made into a cylindrical body, and corresponds to the C-shaped or spiral-shaped blade on the back surface of the disk. A positive displacement fluid machine, characterized in that a spring member is housed inside the guide pin, the spring member protruding from the guide pin for pressing the disk against the backing member in a C-shaped or spiral groove direction. (2) Two sets of the units are arranged back to back with their axes aligned, and the spring member is interposed between the disks of both units, so that each disk serves as a backing member for the opposing disk. 1. A positive displacement fluid machine according to claim 1, characterized in that the displacement fluid machine is configured to also function as a utility model.