JPS5960087A - Volume type hydraulic machine - Google Patents

Abstract

PURPOSE:To improve the stable holding of a contact pressure upon operation as well as a sealing property by a method wherein the contact pressure at a sealing part between the inner and outer peripheral surfaces of each C-type blades and the inside surfaces of a C-type groove, which are opposing to the inner and outer peripheral sufaces of each blades, are made adjustable by the selection of the strength of a spring member. CONSTITUTION:The strengths of the spring members 35..., 36... are selected so that the inner and outer peripheral surfaces 17-20 of each C-type blades 15, 16 can be pushed against the inside surfaces 7-10 of the C-type grooves 3, 4, which are opposing to the blades, and the contact pressures of the sealing parts existing between the inner and outer peripheral surfaces 17-20 and the inside surfaces 7-10 are adjusted properly. Such contact pressures can be obtained by the resilient pressures of the spring members 35..., 36..., therefore, these values may be held in stable upon the operation of the machine and the sealing properties may be held even if the sealing parts are somewhat worn.

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, 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 C-shaped wing is protruded from a disk attached to the open end surface of the groove, and is loosely fitted between the inner surfaces of the C-shaped groove, and whose tip surface is in sliding contact with the bottom surface of the C-shaped groove. is arranged eccentrically by a predetermined distance from the center of curvature of the C-shaped groove so that at least one of the inner and outer circumferential surfaces of the C* blade abuts the inner surface of the C-shaped groove, and If the wing is made to perform a sliding motion that corrects its eccentric trajectory.

Accordingly, a pump unit is provided which is configured to move the fM filling the C-shaped groove from the inlet side to the outlet side. In the following, the poem will be centered around such a C-ring type pump, but in a fluid machine with such a configuration, several sets of the pump units are connected in series, and the C-shaped blades of each of these units are connected in series. By making it possible to operate synchronously with the phases different from each other by a required angle, it is possible to construct a displacement type pump with extremely low pulsation. penetrates each of the above units to forcibly operate the C-shaped blades of each unit, and the operating force can be taken out to the outside.By doing so, it is possible to use a dispersion meter with low pressure loss and a wide range from high speed to low speed. Therefore, it is possible to construct a motor that operates stably over a long period of time.

However, in such a configuration, fM said C type l
Unless the seal between the inner surface of the TY and the inner and outer circumferential surfaces of the C-shaped blade is properly performed, its performance cannot be fully demonstrated. Therefore, in such a fluid machine, the above-mentioned 1 to
In addition to being able to adjust the contact pressure of the seal, it is important that the adjusted contact pressure be stably maintained at a constant value during operation. 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.

The present invention was made with attention to such circumstances, and
A mechanism for causing the C-shaped or spiral-shaped blade to perform a sliding motion is already installed at the axial center of the C-shaped or spiral groove.
a rotating shaft, an eccentric cam that is attached to the outer periphery of the rotating shaft so as to be slidable in a direction that increases or decreases the amount of eccentricity thereof and rotatably engages with the inner periphery of a shaft hole provided in the disk m1; and this eccentric cam. and a spring member provided between the m1 grip rotating shaft and biasing the eccentric cam in the direction of increasing the amount of eccentricity, in order to fully meet the demands mentioned in the IIT. To provide a positive displacement fluid machine.

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

A first pump unit A and a second pump unit B are connected in series. Each pump unit has a C-shaped groove 3.4 opened in one end surface 1a% 2a of the case 1.2, and a disk 5.6 attached to the open end surface of this C-shaped groove 3.4. from the inner surfaces 7 and 8.9 of the C-shaped grooves 3, 4.
A C-shaped blade 15.16 is integrally protruded and is loosely fitted between the C-shaped blade 15.16 and the tip surface 11.12 of the C-shaped blade 15.16 slides in fluid-tight contact with the bottom surface 13.14 of the C-shaped f#3.4, The C-shaped blade is arranged eccentrically by a predetermined distance from the center of curvature O of the C-shaped groove 3.4 so as to be in contact with the inner surface 7.8.9.10 of the 15°-shaped groove.
,, this C-shaped gx5.16 is made to perform a revolving circular motion along its eccentric orbit. ((, 1st period C-shaped groove 3.4 is 3/4 respectively
It has a 10d circular arc shape, and has one end communicating with the inlet 21, z2, and the other end communicating with the outlet 23, 24. Part 1-, the outlet a of the first pump unit A
3 is connected to the inlet 22 of the second pump unit)B. Further, the C-shaped gx5.16 has a 3/4+, 2-arc shape, and the outer inner surface 7.9 of the C-shaped grooves 3, 4 at a predetermined depth position of the C-shaped @3.4. The radius of curvature is moon, and the radius of curvature of the inner inner surface 8.10 is rh.
When R is the average radius of curvature of 5 and 16.

The shape and dimensions are set so that the relational expression R=(rt+rx)/2 holds true. Then, the C-shaped blade 15 of the first pump unit A and the C-shaped '1It16 of the second pump unit B are caused to synchronously move in a synchronous manner with a phase difference of 90 degrees from each other. Furthermore, here, we refer to the state in which the C-shaped blade 15.16 moves so that each part of the C-shaped blade 15.16 moves simultaneously to draw a full circle with the same diameter, and the diameter is , from the width dimension (rt rt) of the C-shaped grooves 3, 6-4, the C-shaped blade 15.1
It corresponds to the value obtained by subtracting the width dimension W of 6. In this embodiment, both pump units A and B are arranged back to back with their axes aligned, and share a rotating shaft 26 inserted through their axes. ! Actuating mechanisms 27, 28 cause each of the C-shaped wings 15, 16 to perform a respective shuffling motion. The wrinkle actuating mechanism 27.28 is attached to the rotary shaft 26 and the outer periphery of the rotary III 126 so as to slide in a direction in which the amount of eccentricity increases or decreases, and is attached to the disk 5.6 via a bearing 29.30. Eccentric cam 3 rotatably secured to the inner periphery of the shaft hole 31, 32
3, 34, and spring members 35, 36, . Specifically, flat surface portions 37 and 38 are formed parallel to the outer circumferential surface of the rotating shaft 26, and the circular surface portions 37 and 38 are slidably fitted in the radial direction. Further, spring holding holes 41..., 42... are provided at the end of m39.40 of the eccentric cam 33.34.
The spring members 35..., 36... stored in the spring holding holes 41..., 42...
, the eccentric cams 33, 34 are biased in a direction in which the amount of eccentricity of the eccentric cams 33, 34 with respect to the rotating shaft 26 increases. That is, due to the biasing force of the spring members 35..., 36...
The inner surfaces 7.8 of the C-shaped grooves 3 and 4 shown in O11
．． I'm trying to push it to 9.10. Also, tiit
A guide plate 43 is disposed between both disks 5 and 6 of both pump units A and B. The guide plate 43 is disk-shaped and has a thick wall portion 43a at its periphery, and the thick wall portion 43a is sandwiched and fixed between the two cases 1.2. Then, on this guide plate 43, which is a member on the case 1.2 side,
A plurality of guide portions 44 having circular cam surfaces 44a on the inner periphery are bored at equal angular intervals in the station placement direction, and each of these guide portions is provided on the disk 5.6 side. The disks 5.6 are respectively engaged with the cam surfaces 44a of the portions 44.
A guide pin 45 is provided to prevent the case from rotating relative to the cases 1 and 2. Each guide pin 45 has a cylindrical shape, and its one end is 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 ffh 11M portion is supported on the back surface of the other disk 6 so as to be able to slide a certain amount in the axial direction. It is supported so that it can slide a certain amount in the direction of the heart. Then, the guide portion 44 is set so that the value obtained by subtracting the diameter of the guide pin 45 from the diameter of the cam surface 44a corresponds to the diameter of the scraping motion of the C-shaped blade 15.16.
... and the dimensions of the guide pin 45... are set. Further, a backing member is arranged 12 facing each other on the back surface of each of the m1 disks 5.6, and this backing member and the mI disk 5.6 are arranged opposite to each other.
A spring member 46 for biasing the two disks 5.6 away from each other is housed in a corresponding C between the disks 5.6 and 5.6. The disk 6 is made to play the role of a backing member, and the other disk 6 is made to play the role of a backing member for the one disk 5.

With such a configuration, the outer circumferential surface 17.18 of the C-shaped blade 15.16 is in line contact with the outer inner surface 7.9 of the C-shaped @3.4 at the outer contact portion shape wing 15
．． Since the inner circumferential surface 19.20 of the C-shaped groove 3.4 is in line contact with the inner inner surface 8.10 on the inside of the C-shaped groove 3.4 in the inner contact part 1, the inside of said C-shaped groove 3.4 is Sickle-shaped spaces 3a, 4a and 51 on the inlet side. Space 3b on the exit side.

It is divided into 4b and 4b. From this autumn, the rotation axis 26
When the C-shaped blade 15.16 is rotated in the direction of arrow Side 7.8
．． 9% 1OrI A transition from the inlet 021゜22 side to the outlet 23.24 side along
3b, 4a, 4b will also move in the same direction, and the fluid filling these rain spaces 3a, 3b14a, 4b will be conveyed from the inlet 21, 221) 111 to the outlet 23, 241. Become. Nine o, Mi said C type g15.
16 performs the Misosuri movement -10-, the time when the external contact part I temporarily disappears (see A of the pump unit of No. 1 in Fig. 4) and I
The timing at which the inner contact portion temporarily disappears (see B in the second pump unit in FIG. 3) occurs periodically. 1. However, the phases of the grinding movements of each of the C-shaped blades 15 and 16 are made to differ between the first pump unit A and the second pump unit B so that these timings do not overlap. Therefore, the inlet 21 of the first pump unit A and the outlet 24 of the second pump unit B are connected to C.
It is said that it communicates with no resistance through the groove 3.4.
His state of affairs is unbelievable even for a moment. No, if it is like this, the fluid sucked in from the if entry inlet 21 will flow into the 11th old IC in both C form 3.4 mf, i+'
! The pumping action of reliably guiding the line 1 to the outlet 24 and sequentially discharging from the outlet 24 can be performed without using any valves or the like.

This kind of operation is obtained, but in this fluid, the inner and outer peripheral surfaces 17, 18, 1 of each C-shaped shank 15, 16
9.20 to the inner surface 7.8.9.1 of the corresponding C-shaped groove 3.4 by the biasing force of the spring members 35, 36...
Since the pressure is to be obtained at 0, by selecting the strength ζ of these spring members 35..., 36..., the inner and outer circumferential surfaces 17, 18, 19.2o and fi
The contact pressure of the sealing portion between the inner surface 7.8.9.10 of the 1T E3 can be adjusted accordingly. still,
Such contact pressure is caused by the spring members 35..., 36
It is obtained by the elastic force of ...-) It is possible to maintain the warpage value stably even during operation, and furthermore,
Even if the seal portion is slightly worn, the contact pressure will not change significantly by φ·1.

In addition, the missing part 11 in the following is a pump and a fluid machine related to this button. However, if the pressure fluid is made to flow through each unit of the FI, this fluid machine can be used as a flow needle or a motor.

In addition, in the embodiment, the case where two sets of units are connected in series is explained.
Ii It also includes those having only one set of the above-mentioned units and those having three or more sets of units.

Furthermore, as described above, the present invention is a scroll type pump equipped with a unit consisting of a combination of a spiral field and a groove, and is capable of applying 41 drops to the motor. An example of this spiral fluid machine is JP-A-51-1
No. 04609 [Compressor-1 Compressor for sexual media] ~τ.

Since the present invention has the above configuration, it is possible to adjust the contact pressure in the sea 3 portion existing between the inner and outer peripheral surfaces of the C-shaped or spiral-shaped blade and the inner surface of the C-shaped or spiral-shaped groove. In addition to being possible, it is possible to provide a positive displacement fluid machine that does not cause the inconvenience that the adjusted contact pressure is stably maintained at a constant value even during operation.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention, and FIG. 1 is a front sectional view;
2 is a cross-sectional view taken along line I-1 in FIG. 1, FIG. 3 is a partial side sectional view, and FIGS. 4 and 5 are diagrams explaining the principle. A, B... Unit (Hump unit) 1.2
...Case 3.4...C-shaped groove 5.6...Disc (true member) 7.8.9.
10...Inner surface 15.16...C-shaped blade 17.18...Inner circumferential surface 19.2o...Outer circumferential surface 21.22... ... Inflow port 23.24 ... Outlet port 26 ... Rotating shaft 27.28 ... True operation mechanism 33.34 ... Eccentric cam 35. 36...Spring member agent Patent attorney Hirokazu Akazawa 14-

Claims (1)

[Claims] The opening of this C-shaped or spiral-shaped groove [1-] is attached to the end surface of the disk, and the distal end of the C-shaped or spiral-shaped groove fits loosely between the inner surfaces of the C-shaped or spiral-shaped groove. A C-shaped or spiral-shaped blade is provided protrudingly in close contact with the bottom surface of the C-shaped or spiral-shaped blade, and at least one of the inner peripheral surface and the outer peripheral surface of the C-shaped or spiral-shaped blade is formed into the C-shaped or spiral groove. The C-shaped or spiral-shaped groove is arranged eccentrically by a predetermined distance from the center of curvature so as to come into contact with the inner surface of the groove, and a blade actuation mechanism is used to apply a sliding movement to the C-shaped or spiral-shaped blade by an amount of eccentricity aLtcc. By doing this, Ifi the cylindrical shape transfers the fluid filling the spiral groove from the inlet side to mI.
Move to the recording outlet side! : A positive displacement fluid machine comprising a unit configured to obtain the blade operating mechanism, a rotating shaft disposed at the axial center of the C-shaped or spiral groove, and a rotating shaft of the rotating shaft. 1. A displacement fluid machine comprising: a spring member mounted on the outer periphery so as to be slidable in a direction in which the eccentricity increases or decreases, and biases the eccentric cam in a direction in which the eccentricity increases.