JPH11324899A - Pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pump which has a simple structure, can suitably supply low-fluidity fluid, is easily disassembled, and can easily perform cleaning of the inside. SOLUTION: A piston 6 is resiprocatively accommodated in a through cylinder 5 of a rotor cylinder 4 rotatable in housings 2a, 2b, 2c. An intermittent rotation mechanism (including a locking projection 18, locking ball storing holes 20A, 20B, locking balls 22A, 22B, and a locking ball refuge recessed part 24) for interrupting rotational force according to rotation angle of a driving shaft 16 is interposed between the driving shaft 16 and the rotor cylinder 4 inserted into the housings. The driving shaft 16 is rotated, while rotation of the rotor cylinder 4 is stopped, the piston 6 is moved, the fluid is sucked through a suction opening 10, the fluid is discharged through a delivery opening 12, and while the rotor cylinder 4 is rotating, movement of the piston 6 to the through cylinder 5 is stopped.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump technology, and more particularly to a structure of a pump suitably used for stably supplying a fluid having high viscosity or low fluidity. Examples of the supplied fluid include food materials.

[0002]

2. Description of the Related Art In the food manufacturing industry, liquid food materials such as bubu-an, okara, boiled beans for natto production, fish meat pickles for kamaboko production, and various cooking food ingredients (gyoza) , Shumai,
Ingredients such as hamburger steaks and croquettes are often handled. Materials having such fluidity (fluids)
After preparation, it is sent for subdivision packaging and the like. Conventionally, such feeding has been performed using a vane type (paddle type) pump.

[0003] However, when the viscosity of the fluid is high and the fluidity is low, the conventional vane-type pump described above may not be able to supply the fluid sufficiently. In particular, when the fluid is the food material, frequent cleaning of the inside of the pump is required from the viewpoint of food hygiene.

Therefore, an object of the present invention is to provide a simple structure,
An object of the present invention is to provide a pump capable of supplying a high-viscosity or low-fluidity fluid satisfactorily.

Another object of the present invention is to provide a pump that can be easily disassembled and can easily perform internal cleaning.

[0006]

According to the present invention, in order to achieve the above object, a rotary cylinder is housed in a housing so as to be rotatable around a center of rotation, and a through cylinder of the rotary cylinder is provided. A piston is accommodated therein so as to be relatively reciprocable in a direction non-parallel to the direction of the rotation center, and the housing is formed by the housing, the penetrating cylinder, and both ends of the piston. An inlet and an outlet are formed so as to be able to communicate with the two variable volume spaces, and a drive shaft is inserted into the housing, and the drive shaft is provided between the drive shaft and the rotary cylinder. An intermittent rotation mechanism intermittently rotating the rotary cylinder around the rotation center by intermittently transmitting torque according to the rotation angle of the shaft is interposed. Between the shaft and the piston,
An intermittent moving mechanism that moves the piston with respect to the penetrating cylinder while the rotation of the rotary cylinder is stopped by the action of the intermittent rotating mechanism is provided,
By rotating the drive shaft, while the rotation of the rotary cylinder is stopped by the action of the intermittent rotation mechanism, the piston is moved relative to the penetrating cylinder by the action of the intermittent movement mechanism, One of the two variable volume spaces is increased to suck the fluid through the suction port, and the other volume of the two variable volume spaces is reduced to discharge the fluid through the discharge port. A pump configured to stop the movement of the piston with respect to the penetrating cylinder by the operation of the intermittent moving mechanism while the rotary cylinder is rotating by the operation of the intermittent rotation mechanism. Provided.

In one aspect of the present invention, the direction of relative movement of the piston with respect to the penetrating cylinder is orthogonal to the direction of the center of rotation.

In one aspect of the present invention, the intermittent rotation mechanism comprises: an engagement protrusion provided on an outer peripheral surface of the drive shaft;
A pair of engagement piece receiving holes provided in the rotary cylinder on opposite sides with respect to the rotation center, and accommodated in the pair of engagement piece accommodation holes so as to be movable in a radial direction of the drive shaft. A pair of engaging pieces engageable with the engaging projections, and an engaging piece retreating recess provided in the housing, wherein one of the pair of engaging pieces is the engaging piece. When at the position corresponding to the frame retreating recess, the engaging projection is configured to avoid engagement with the engaging piece, and the engaging piece at the position corresponding to the engaging piece retreating recess is When the rotary cylinder rotates, it is held in the engaging piece receiving hole and is detached from the engaging piece retreating concave portion.

In one aspect of the present invention, the engagement between the engagement protrusion and the engagement piece is performed by point contact, line contact, or surface contact.

[0010] In one embodiment of the present invention, the engagement piece is a spherical engagement ball.

In one aspect of the present invention, the intermittent moving mechanism includes a circular cam member provided on the drive shaft, a notch formed in the piston and engaged with the circular cam member in the direction of the piston. And an engaging portion.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is an exploded perspective view showing an embodiment of a pump according to the present invention, and FIGS. 2 and 3 are sectional views showing an assembled state thereof.

In these figures, reference numeral 2a denotes a housing main body, 2b and 2c denote housing lids, and the housing lids 2b and 2c are fixed to the housing main body 2a by bolts. These main parts 2
a and the lid 2b, 2c constitute the housing 2.

A rotary cylinder 4 is provided in the housing 2.
Is arranged. The rotary cylinder 4 includes a cylinder portion 4a having a substantially cylindrical outer shape, and a substantially cylindrical rotational driving force transmission portion 4b attached to one end of the cylinder portion in the Z direction. The rotary cylinder 4 is rotatable about a rotation center R in the Z direction in the housing 2. The cylinder portion 4a of the rotary cylinder 4 has a Z
A penetrating cylinder 5 having a circular cross section is formed in a direction perpendicular to the direction (Y direction in FIG. 1). A piston 6 is housed in the penetrating cylinder 5, and the piston 6 can reciprocate in the penetrating cylinder 5 in the direction (Y direction in FIG. 1). The piston 6 has a notch engaging portion 8 formed by cutting out a half portion in the Z direction at a substantially central portion in the direction.

A drive shaft 16 connected to a motor output rotary shaft (not shown) is inserted into the housing 2 through the housing cover 2b. This drive shaft 1
Numeral 6 is supported on the housing lids 2b and 2c via bearings, respectively, so as to be rotatable around the rotation center R in the Z direction. A peripheral surface cam member 17 is formed on the drive shaft 16. The cam member 17 is XY
The cross-sectional shape in the plane (that is, the shape viewed in the Z direction) is circular, and its diameter is slightly smaller than the dimension of the notch engaging portion 8 in the Y direction. Have been combined. The center of symmetry S of the cam member 17 is eccentric from the center of rotation R. The drive shaft 16 is provided with an engagement projection 18 at a position in the Z direction corresponding to the rotational drive force transmitting portion 4b of the rotary cylinder 4. The rotation center R
The position of the engagement protrusion 18 in the circumferential direction around is a position shifted by 90 degrees from the position (circumferential position) of the symmetry center S around the rotation center R.

However, in FIGS. 2 and 3, for convenience of explanation, the engagement projections in different states are also indicated by reference numeral 18 'in the upper half.

Rotary driving force transmitting section 4 of rotary cylinder 4
In FIG. 2B, engaging ball receiving holes 20A and 20B are formed at two circumferential positions different from each other by 180 degrees around the rotation center R. These engagement ball receiving holes 20A, 20B
Penetrates the rotary driving force transmitting portion 4b in the radial direction (radial direction of the rotating shaft 16 having the rotation center R), and the engaging ball receiving holes 20A and 20B respectively
A and 22B are accommodated so as to be movable in the radial direction.

In the housing lid 2c, one engaging ball retreating recess 24 is formed at a position in the Z direction corresponding to the engaging ball receiving holes 20A and 20B.

The cylinder portion 4a of the rotary cylinder 4
In addition, a cavity through which the drive shaft 16 penetrates is formed in the rotary driving force transmission unit 4b. This space is formed with dimensional allowance so that the drive shaft 16 can be inserted and withdrawn from the housing lid 2b side and the inserted drive shaft 16 can be rotated. The drive shaft 16 extends through the long hole 9 formed in the piston 6. The length of the long hole is set so as to allow the piston 6 to reciprocate with the required stroke with respect to the penetrating cylinder 5.

The housing main body 2a can communicate with two variable capacity spaces formed by the housing main body 2a, the penetrating cylinder 5 of the rotary cylinder 4, and both ends of the piston 6 (both ends in the Y direction in FIG. 1). Like, Y
The suction port 10 and the discharge port 1
2 are formed.

Next, the operation of this embodiment will be described with reference to FIGS. 4 and 5 and FIGS. FIG. 4 shows the eccentric rotation of the cam member 17 and the rotation of the cylinder portion 4 a of the rotary cylinder 4 (the through cylinder 5
And the movement of the piston 6 in the penetrating cylinder 5 of the cylinder portion 4a. FIG.
Is the rotation of the cylinder 4a of the rotary cylinder 4 due to the rotation of the drive shaft 16 and the movement of the piston 6 in the penetrating cylinder 5 of the cylinder 4a. Circumferential movement of the projection 18 and rotation of the rotational driving force transmitting portion 4b (engagement ball receiving holes 20A, 20A).
B) and engagement ball receiving hole 20
2A and 2B show how engagement balls 22A and 22B in the engagement projections 18 are engaged with the engagement balls 22A and 22B. FIG. 4 (a) and FIG.
4A shows a case where the rotation angle [set for convenience] of the drive shaft 16 around the rotation center is 0 degrees, and FIG.
5B shows a case where the rotation angle of the drive shaft 16 around the rotation center is 90 degrees, and FIG. 4C and FIG.
4D shows a case where the rotation angle of the drive shaft 16 around the rotation center is 180 degrees, and FIGS. 4D and 5D show a case where the rotation angle of the drive shaft 16 around the rotation center is 270 degrees. 4 (e) and 5 (e) show the case where the rotation angle of the drive shaft 16 around the rotation center is 360 degrees.

When the rotation angle of the drive shaft 16 is 0 degree,
As shown in FIGS. 4A and 5A, the piston 6 and the penetrating cylinder 5 are oriented in the horizontal direction, the suction port 10 communicates with the first variable volume space C1, and the discharge port 1
2 and the second variable volume space C2 communicate with each other. Due to the engagement relationship between the notch engagement portion 8 of the piston 6 and the cam member 17,
The volume of the first variable volume space C1 is larger than the volume of the second variable volume space C2 (in FIG. 4A, the center of symmetry S is to the right of the rotation center R, and the volume of the first variable volume space C1 is possible. The maximum value, and the volume of the second variable volume space C2 is the smallest possible value).

In this state, the fluid is sucked through the suction port 10 into the first variable volume space C1. Also,
The engagement protrusion 18 is located above the rotation center R, and abuts against the engagement ball 22A in the engagement ball accommodation hole 20A from the inside in the radial direction and from behind in the rotation direction. The engagement ball 22A is located between the outer peripheral surface of the drive shaft 16 and the inner peripheral surface of the housing lid 2c at the Z-direction position where the engagement protrusion 18 is formed. On the other hand, one half of the engaging ball 22B is located in the engaging ball retracting recess 24, and the other half is located in the engaging ball receiving hole 20B. That is, in this state, the engagement ball 22B has moved to a position separated from the outer peripheral surface of the drive shaft 16.

When the drive shaft 16 rotates clockwise by an angle of 90 degrees from the state shown in FIGS. 4A and 5A, the engagement between the engagement ball receiving hole 20A of the rotary drive force transmitting portion 4b is established. When the engaging projection 18 pushes the combined ball 22A in the circumferential direction (in the direction of rotation), the rotational driving force transmitting unit 4b rotates clockwise by an angle of 90 degrees (at this time, the rotational driving force transmitting unit 4b rotates). As a result, the other engaging ball 22B is pushed in the circumferential direction by the engaging ball housing hole 20B, whereby the other engaging ball 22B is pressed against the wall surface (formed as a slope) of the engaging ball retreating concave portion 24, and the rotation center R gradually increases. To move away from the engaging ball retreating concave portion 24 and then to the drive shaft 16.
Is maintained in the engaging ball receiving hole 20B between the outer peripheral surface of the housing and the inner peripheral surface of the housing lid 2c.
Degrees). As a result, the cylinder portion 4a of the rotary cylinder 4 also rotates clockwise at an angle of 90 degrees, and the direction of the penetrating cylinder 5 and the direction of the piston 6 also rotate clockwise at an angle of 90 degrees.
Rotate degrees. At the same time, the center of symmetry S of the cam member 17 rotates clockwise around the center of rotation R by an angle of 90 degrees.

Thus, when the rotation angle of the drive shaft 16 is 90 degrees, as shown in FIGS. 4B and 5B, the piston 6 and the penetrating cylinder 5 are oriented vertically. I have. In this state, both the first variable volume space C1 and the second variable volume space C2 are
Has been cut off. In addition, the first variable volume space C1
4 and the volume of the second variable volume space C2 are both shown in FIG.
This is the same as the state shown in FIG.

Next, when the drive shaft 16 rotates clockwise by an angle of 90 degrees from the state shown in FIGS. 4B and 5B, the engagement ball receiving hole 20A of the rotary drive force transmitting portion 4b is rotated. When the engaging projection 18 pushes the engaging ball 22A in the circumferential direction (in the direction of rotation), the rotational driving force transmitting portion 4b rotates clockwise by an angle of 90 degrees (in this case, the other engaging ball 22A).
B is maintained in the engagement ball receiving hole 20B and rotates clockwise by 90 degrees.) Thus, the cylinder portion 4a of the rotary cylinder 4 also rotates clockwise by 90 degrees, and the direction of the penetrating cylinder 5 and the direction of the piston 6 also rotate clockwise by 90 degrees. At the same time, the center of symmetry S of the cam member 17 rotates clockwise around the center of rotation R by an angle of 90 degrees.

Thus, the rotation angle of the drive shaft 16 becomes 180
In the case of the degree, as shown in FIG. 4C and FIG. 5C, the piston 6 and the penetrating cylinder 5 are oriented in the horizontal direction. In this state, the suction port 10 communicates with the second variable volume space C2, and the discharge port 12 communicates with the first variable volume space C2.
1 is in communication. Further, both the volume of the first variable volume space C1 and the volume of the second variable volume space C2 are shown in FIG.
This is the same as the state shown in FIG.

When the rotation angle of the drive shaft 16 is 180 degrees, as shown in FIG. 5C, the engaging ball 22A is located at a circumferential position corresponding to the engaging ball retracting recess 24. Then, it is pushed into the engaging ball retreating concave portion 24 by pressing by the engaging projection 18. This engagement ball 22
The movement of A to the engaging ball retreating concave portion 24 is favorably performed by the engaging ball retreating concave portion 24 being located below the engaging ball receiving hole 20A and the gravity acting on the engaging ball 22A.

Next, when the drive shaft 16 rotates clockwise by an angle of 90 degrees from the state shown in FIGS. 4C and 5C, half of the engaging ball 22A is used to retract the engaging ball. Recess 2
4 and the other half is located in the engaging ball receiving hole 20A, so that the engaging protrusion 18 can pass in the circumferential direction without engaging with the engaging ball 22A, and thus the rotational driving force transmitting portion 4b , The rotational force of the drive shaft 16 is not transmitted. Accordingly, the direction of the penetrating cylinder 5 formed on the cylinder portion 4a of the rotary cylinder 4 and the direction of the piston 6 accommodated therein also remain horizontal. On the other hand, the center of symmetry S of the cam member 17 rotates clockwise by 90 degrees around the center of rotation R.

Thus, the rotation angle of the drive shaft 16 becomes 270
In the case of the degree, as shown in FIGS. 4 (d) and 5 (d), similar to the state of FIGS. 4 (c) and 5 (c),
The piston 6 and the penetrating cylinder 5 are oriented in the horizontal direction, and the suction port 10 communicates with the second variable volume space C2, and the discharge port 12 communicates with the first variable volume space C1. However, due to the engagement relationship between the notch engagement portion 8 of the piston 6 and the cam member 17, the volume of the first variable volume space C1 is reduced as compared with the state of FIGS. 4C and 5C. Second
The volume of the variable volume space C2 is increasing. This figure 4
5D and FIG. 5D, the first variable volume space C
1 and the volume of the second variable volume space C2 are substantially equal.

Next, when the drive shaft 16 rotates by 90 degrees clockwise from the state shown in FIGS. 4D and 5D, except for the last slight angle range, FIG. As in the case of shifting from the state of FIG. 5C and FIG. 5C to the state of FIG. 4D and FIG. 5D, the rotational force is not transmitted to the rotational driving force transmitting unit 4b. Accordingly, the direction of the penetrating cylinder 5 formed on the cylinder portion 4a of the rotary cylinder 4 and the direction of the piston 6 accommodated therein also remain horizontal. However, in the last slight angle range, the rotation driving force transmission portion 4b is pushed by the engagement projection 18 pressing the engagement ball 22B in the engagement ball accommodation hole 20B in the circumferential direction (in the direction of rotation). Rotate a slight angle clockwise.
On the other hand, the center of symmetry S of the cam member 17 rotates clockwise by 90 degrees around the center of rotation R.

Thus, the rotation angle of the drive shaft 16 becomes 360
In the case of degrees, as shown in FIGS. 4 (e) and 5 (e), similar to the states of FIGS. 4 (d) and 5 (d),
The piston 6 and the penetrating cylinder 5 are oriented in the horizontal direction, and the suction port 10 communicates with the second variable volume space C2, and the discharge port 12 communicates with the first variable volume space C1. However, due to the engagement relationship between the notch engagement portion 8 of the piston 6 and the cam member 17, the volume of the first variable volume space C1 is reduced as compared with the state of FIGS. 4D and 5D. Second
The volume of the variable volume space C2 is increasing. This figure 4
5 (e) and FIG. 5 (e), the first variable volume space C
4 is smaller than the second variable volume space C2 (FIG. 4).
In (e), the center of symmetry S is to the right of the center of rotation R,
The volume of the first variable volume space C1 is the smallest possible value, and the volume of the second variable volume space C2 is the largest possible value).

4 (e) and 5 (e) are as follows.
FIGS. 4A and 5A show the first variable volume space C1.
And the second variable volume space C2 alternates, the engaging ball receiving hole 20A and the engaging ball receiving hole 20B alternate, and the engaging ball 22A and the engaging ball 22B alternate.
Therefore, when the drive shaft 16 is again rotated clockwise around the rotation center R by an angle of 360 degrees, the drive shaft 16 shown in FIGS.
In the operation described with reference to FIG. 5E and FIGS. 5A to 5E, the first variable volume space C1 and the second variable volume space C2 are alternated, and the engagement ball accommodating holes 20A and 20B And the engaging ball 22A and the engaging ball 2
An operation in which 2B is replaced is performed. Hereinafter, the same operation is continued.

The state shown in FIGS. 4 (c) and 5 (c) is changed to the state shown in FIGS. 4 (e) and 5 (e) through the states shown in FIGS. 4 (d) and 5 (d). In the process, the fluid contained in the first or second variable volume space C1, C2 communicating with the discharge port 12 is discharged through the discharge port 12 due to the reduction in the volume of the variable volume space C1, C2. , At the same time, the second or first variable volume space C communicating with the suction port 10
Fluid is sucked into the variable volume spaces C2 and C1 via the suction port 10 due to the increase in the volume of the volumes C2 and C1.

In the present embodiment, on the other hand, the rotational force of the drive shaft 16 is applied to the engagement member 18 and the engagement ball accommodation holes 20A, 20A.
B, the rotation is transmitted to the rotary cylinder 4 via an intermittent rotation mechanism using the engagement balls 22A and 22B and the engagement ball retreating concave portion 24, thereby realizing the intermittent rotation of the rotary cylinder 4; The rotational force is transmitted to the piston 6 through a cam mechanism using the cam member 17 and the notch engaging portion 8 to realize the reciprocating movement of the piston 6 with respect to the rotary cylinder 4. Thus, when the rotary cylinder 4 rotates, the movement of the piston 6 with respect to the rotary cylinder 4 is stopped, and during this time, the suction fluid in the variable volume space that communicates with the suction port 10 communicates with the discharge port 12. Position, and while the rotation of the rotary cylinder 4 is stopped, the piston 6 is moved with respect to the rotary cylinder 4 to suck the fluid into the variable volume space communicating with the suction port 10 and the discharge port 12. The fluid is discharged from the variable volume space communicating with the fluid.

Thus, the fluid is not compressed or expanded in the pump, the properties of the fluid are maintained stably, and a good fluid supply becomes possible.

In this embodiment, no special valve opening / closing operation is required, and no special mechanism is required. Furthermore, in this embodiment, the number of components can be significantly reduced. Thus, according to the present embodiment, cost reduction is realized. Further, even a fluid having a high viscosity or a low fluidity can be satisfactorily supplied.

Further, in this embodiment, when disassembling and reassembling the apparatus for internal cleaning, maintenance and inspection, etc., it is easy to remove the bolts from the housing lids 2b and 2c only by the operation of FIG. And the reassembly is similarly easy.

In this embodiment, since the fluid discharge from the discharge port 12 is intermittent, the fluid cutting means is arranged adjacent to the discharge port 12 so that By operating at the timing, it is possible to easily supply the fluid by dividing it into small portions.

In the above embodiment, a spherical engaging ball is used as the engaging piece. However, in the present invention, if the engaging ball has the function of the engaging ball as described in the above embodiment, Other shapes such as a convex spherical shape, a truncated cone shape, or a truncated pyramid shape at both end surfaces, a cylindrical shape or a prism shape at the center portion, and a shape which is accommodated in the engagement piece housing hole so as to be movable in the longitudinal direction thereof. It is also possible to use as a combination piece.

Further, in the above embodiment, the engagement between the engagement ball as the engagement piece and the engagement projection is performed by point contact.
In the present invention, for example, a columnar member arranged in parallel with the direction of the rotation center R is used as the engaging piece (the engaging piece receiving hole and the engaging piece retreating recess are appropriately formed corresponding to the shape of this engaging piece). By using an engagement protrusion having an engagement surface extending parallel to the direction of the rotation center R,
The engagement between the engagement piece and the engagement protrusion can be performed by line contact. Further, for example, an engagement piece having a first engagement surface extending parallel to the direction of the rotation center R is used (an engagement piece accommodation hole and an engagement piece retreating recess correspond to the shape of this engagement piece). By using an engagement projection having a second engagement surface extending in parallel to the direction of the rotation center R, the engagement between the engagement piece and the engagement projection can be performed. Surface contact can be made at positions other than the retracting concave position. In this manner, by making the engagement between the engagement piece and the engagement projection a line contact or a surface contact at least at a position other than the engagement piece retreating concave position, the force acting on the engagement piece and the engagement projection when transmitting the driving force is obtained. Can be dispersed to reduce the pressure, and the transmittable torque can be increased.

[0043]

As described above, according to the present invention, there is provided a pump which has a simple structure, is easy to manufacture at low cost, and can supply a high viscosity or low fluidity fluid. Further, according to the present invention, there is provided a pump which is easy to disassemble and assemble.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view showing an embodiment of a pump according to the present invention.

FIG. 2 is a sectional view showing an assembled state of an embodiment of the pump according to the present invention.

FIG. 3 is a sectional view showing an assembled state of an embodiment of the pump according to the present invention.

FIG. 4 is an operation explanatory view of one embodiment of the pump according to the present invention.

FIG. 5 is an operation explanatory view of one embodiment of the pump according to the present invention.

[Explanation of symbols]

 2 Housing 2a Housing main body part 2b, 2c Housing lid body part 4 Rotary cylinder 4a Cylinder part of rotary cylinder 4b Rotary driving force transmission part of rotary cylinder 5 Penetrating cylinder 6 Piston 8 Notch engaging part 9 Slot 10 Suction port 12 Discharge port DESCRIPTION OF SYMBOLS 16 Drive shaft 17 Cam member 18 Engagement projection 20A, 20B Engagement ball accommodation hole 22A, 22B Engagement ball 24 Engagement ball retreating recess C1 First variable volume space C2 Second variable volume space R Rotation center S Symmetry center

Claims (6)

[Claims] 1. A rotary cylinder is accommodated in a housing so as to be rotatable around a rotation center, and a rotary cylinder reciprocates in a penetrating cylinder of the rotary cylinder in a direction non-parallel to the direction of the rotation center. A piston is housed so as to be movable, and the housing has an inlet and an outlet so as to be able to communicate with two variable volume spaces formed by the housing, the penetrating cylinder, and both ends of the piston. A drive shaft is inserted into the housing, and the rotary cylinder is interposed between the drive shaft and the rotary cylinder in accordance with a rotation angle of the drive shaft to transmit and receive rotational force. An intermittent rotation mechanism for intermittently rotating the rotation shaft around the rotation center is interposed between the drive shaft and the piston by the action of the intermittent rotation mechanism. An intermittent moving mechanism for moving the piston with respect to the penetrating cylinder while the rotation of the rotary cylinder is stopped is provided. By rotating the drive shaft, the rotary mechanism is operated by the action of the intermittent rotating mechanism. While the rotation of the cylinder is stopped, the piston is moved with respect to the penetrating cylinder by the action of the intermittent moving mechanism to increase one volume of the two volume variable spaces and through the suction port. While the rotary cylinder is rotating by the action of the intermittent rotation mechanism, the fluid is sucked and the other volume of the two variable volume spaces is reduced so that the fluid is discharged through the discharge port. And a pump configured to stop the movement of the piston with respect to the penetrating cylinder by an operation of the intermittent moving mechanism. 2. The pump according to claim 1, wherein a direction of a relative movement of the piston with respect to the penetrating cylinder is orthogonal to a direction of the rotation center. 3. The intermittent rotation mechanism includes: an engagement projection provided on an outer peripheral surface of the drive shaft; and a pair of engagement piece housing holes provided on the rotary cylinder on opposite sides with respect to the rotation center. A pair of engagement pieces accommodated in the pair of engagement piece accommodation holes so as to be movable in the radial direction of the drive shaft and engageable with the engagement projections; A concave portion for retreating a combination piece, wherein when one of the pair of engaging pieces is at a position corresponding to the concave portion for retracting the engaging piece, the engaging projection engages with the engaging piece. The engaging piece at a position corresponding to the engaging piece retreating recess is held in the engaging piece receiving hole by rotation of the rotary cylinder, and the engaging piece retreat The concave portion is detached from the concave portion. Pump according to any one. 4. The pump according to claim 3, wherein the engagement between the engagement protrusion and the engagement piece is performed by point contact, line contact, or surface contact. 5. The pump according to claim 3, wherein the engagement piece is a spherical engagement ball. 6. The intermittent moving mechanism has a circular cam member provided on the drive shaft, and a notch engaging portion formed on the piston and engaged with the circular cam member in the direction of the piston. The pump according to claim 1, wherein the pump is a pump.