JP2012096013A - Oil supply pump for sewing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply pump that eliminates the need to fill a cylinder with a lubricant in advance.SOLUTION: An oil supply pump comprises: a plunger 30 that makes advance/return movements by means of a motion conversion mechanism 20; a pump body 40 having a cylinder part 41; a flow-inlet side check valve 50 that allows a lubricant flow only in the direction of flowing into the cylinder part; and a flow-outlet side check valve 60 that allows a lubricant flow only in the direction of flowing out of the cylinder part. The flow-inlet side check valve and the flow-outlet side check valve both comprise plate-like valve bodies 51 and 61 that open a flow channel as they are elastically bent in predetermined directions, and plate-like restriction bodies 53 and 63 provided at the upstream in the lubricant flow directions with respect to the valve bodies to restrict the bend of the valve bodies toward the upstream in the lubricant flow directions. In addition, the flow-inlet side check valve comprises a flow inlet port 75A, while the flow-outlet side check valve comprises a valve body 91 supported by a coil spring 92. The plate-like valve body 51 and the plate-like restriction body 63 are formed in a single flat plate 81, while the plate-like valve body 61 and the plate-like restriction body 53 are formed in another flat plate 83. One, two or three flat plates are disposed as stacked on the pump body.

Description

  The present invention relates to an oil supply pump for circulating lubricating oil in a sewing machine.

  Conventionally, industrial sewing machine mechanisms are used at high speeds, and therefore require lubricating oil on sliding surfaces such as shuttle mechanisms and metal bearings. If there is insufficient lubricating oil in these portions, not only the operation is not smoothly performed, but also seizure may occur. Therefore, many sewing machines are provided with an oil supply pump for supplying lubricating oil so that these parts are constantly supplied with oil.

  As shown in FIG. 12, the oil pump 100 includes an eccentric cam 102 fixedly mounted on a lower shaft 101 that rotates using a sewing machine motor as a drive source, and a piston that reciprocates by the action of the eccentric cam 102 and the return spring 103. 104, a cylinder block 106 in which a cylinder portion 105 into which the piston 104 is inserted is formed, and an inflow provided in valve chambers 107 and 108 formed on one side and the other side of the cylinder block 106 with the cylinder portion 105 interposed therebetween. Side and outflow side check valves 109 and 110 are provided.

The return spring 103 of the oil pump 100 is disposed inside the cylinder portion 105.
Further, the check valve 109 on the inflow side includes a ball valve 112 provided in the valve chamber 107 so as to allow only the flow in the inflow direction to the cylinder portion 105 by the pressing spring 111, and the reverse valve on the outflow side is provided. The stop valve 110 includes a ball valve 114 provided in the valve chamber 108 so as to allow only the flow in the outflow direction to the cylinder portion 105 by the pressing spring 113 (see, for example, Patent Document 1).

JP 2010-082150 A

However, since the conventional oil feed pump 100 of the sewing machine has a configuration in which the check valves 109 and 110 include ball valves 112 and 114 and pressing springs 111 and 113, valve chambers 107 and 108 for arranging them are provided. There is a problem that it is essential and it is difficult to reduce the size of the pump.
Further, since the oil feed pump 100 of the sewing machine is provided with the return spring 103 in the cylinder portion 105, the cylinder portion 105 is returned to the return spring 103 even when the piston 104 is retracted most (when located at the bottom dead center). It is necessary to secure the minimum volume necessary to secure the installation space of the cylinder, and because the two valve chambers 107 and 108 described above are provided in the cylinder part, the air in the cylinder part 105 is obtained. When there is even a small amount of gas such as, there is a problem that the pump efficiency is drastically reduced by contracting only the gas.
Accordingly, even if the sewing machine motor is driven from a state where no lubricating oil is contained in the cylinder part 105, the lubricating oil cannot be circulated by the oil supply pump 100. If the oil is drained, when the oil supply pump 100 is re-driven, there is a problem that an operator needs to manually fill the cylinder portion 105 with lubricating oil in advance.

  An object of the present invention is to provide an oil pump for a sewing machine that can supply lubricating oil with a simple configuration.

According to a first aspect of the present invention, there is provided an operation conversion mechanism that converts torque of a drive shaft that rotates using a sewing machine motor as a drive source into a linear motion reciprocating operation, a plunger that moves forward and backward by the operation conversion mechanism, and a forward and backward movement of the plunger. A pump body that is movably supported and includes a cylinder part, an inflow check valve that communicates with the cylinder part and allows only the flow of lubricating oil in the direction of flowing into the cylinder part, and communicates with the cylinder part In addition, in the oil supply pump of the sewing machine provided with an outflow check valve that allows only the flow of the lubricating oil in the direction of flowing out from the cylinder portion, the inflow check valve and the outflow check valve are both A valve body, and a regulating body provided with a passage for lubricating oil that can be closed by the valve body on the upstream side in the flow allowable direction of the valve body,
One of the inflow check valve and the outflow check valve is a plate-shaped member that opens as a valve body by elastically deflecting toward the downstream side in the allowable flow direction of the lubricating oil as the valve body. A valve body is provided.

  The invention according to claim 2 has the same configuration as that of the invention according to claim 1, and both the inflow check valve and the outflow check valve include the plate-shaped valve body, The valve body of the side check valve and the regulating body of the outflow side check valve are formed on the same flat plate, and the regulating body of the inflow side check valve and the valve body of the outflow side check valve are the same other The two flat plates are stacked on the pump main body and provided side by side.

  The invention described in claim 3 has the same configuration as that of the invention described in claim 2, and the two flat plates are formed in the same shape and structure, and the valve body of one flat plate and the restriction of the other flat plate. The body is opposed, and the regulating body of one flat plate and the valve body of the other flat plate are overlapped so as to face each other, and the pump body is provided.

  The invention described in claim 4 has the same configuration as that of the invention described in claim 2 or 3, and further includes a base disposed below the pump main body and fixed to the pump main body. Is formed so that the bottom thereof is opened, and the two flat plates are sandwiched between the pump main body and the base to close the opened bottom, and the plunger is pumped by the motion conversion mechanism. It is moved to the extent that it touches the flat plate on the main body side.

  The invention according to claim 5 has the same configuration as that of the invention according to any one of claims 2 to 4, and each of the valve bodies and each of the regulating bodies is provided between the two flat plates. And a flat plate provided with a throttle hole for adjusting the flow rate of the lubricating oil in an arrangement between the two.

  The invention described in claim 6 has the same configuration as that of the invention described in claim 1, the inflow side check valve includes the plate-shaped valve body, and the outflow side check valve includes the outflow valve. A valve body and a coil spring disposed on the downstream side of the regulating body of the side check valve, the coil spring pressing the valve body against the regulating body, and the passage opening provided in the regulating body is closed. In addition, the passage opening is opened by causing the valve body to be separated from the regulating body by contraction deformation of the coil spring.

  The invention according to claim 7 has the same configuration as that of the invention according to claim 6, and the valve body of the inflow check valve and the regulating body of the outflow check valve are formed on the same flat plate. The flat plate is formed so as to overlap the pump body.

  The invention described in claim 8 has the same configuration as that of the invention described in claim 7, and further includes a base disposed below the pump main body and fixed to the pump main body. The bottom is formed so as to open, and the flat plate is sandwiched between the pump main body and the base to close the opened bottom, and the plunger moves to the extent that it contacts the flat plate by the motion conversion mechanism. The restriction body of the inflow check valve is configured by the base.

  The invention described in claim 9 has the same configuration as that of any one of claims 2 to 4 and claims 7 to 8, and the flat plate is formed of a spring steel material. To do.

  The invention according to claim 10 has the same configuration as the invention according to any one of claims 1 to 9, and the motion conversion mechanism is only in one of the forward and backward movement directions with respect to the plunger. And a return spring that applies a moving force in the remaining direction of the forward / backward movement direction is provided on the plunger, and the return spring is disposed outside the cylinder portion.

  The invention according to claim 11 has the same configuration as that of the invention according to any one of claims 1 to 10, and the motion conversion mechanism is an eccentric cam fixedly mounted on the drive shaft, The inflow side check valve and the outflow side check valve are arranged side by side in a direction orthogonal to the drive shaft, and the cross-sectional shape viewed from the forward / backward movement direction of the plunger is elongated along the direction orthogonal to the drive shaft. It is characterized by the following shape.

  The invention described in claim 12 has the same configuration as that of the invention described in claim 11, and is provided on the outer periphery of the plunger, and seals between the inner peripheral surface of the cylinder part and the outer peripheral surface of the plunger. The O-ring includes a ring, and the shape of the O-ring without any external force is an oval shape that is long in one direction and flattened in a direction orthogonal to the cross-sectional shape of the plunger.

  The invention according to claim 13 has the same configuration as that of the invention according to any one of claims 1 to 12, and is provided on the outer periphery of the plunger, and the inner peripheral surface of the cylinder portion and the outer periphery of the plunger A plurality of O-rings sealing between the surfaces are provided, and the plurality of O-rings are arranged at different positions with respect to the forward / backward movement direction axis of the plunger.

In the present invention, since the inflow check valve or the outflow check valve is formed by a flat plate, the plate check valve is thinned and the valve chamber is almost unnecessary, so that the pump as a whole is greatly reduced. It is possible to realize a small size.
Further, since the valve body and the regulating body are formed by processing the flat plate, it is possible to facilitate processing and manufacturing.

In particular, the cross-sectional shape seen from the forward / backward movement direction of the plunger is long along the direction orthogonal to the drive shaft, and the inflow check valve and the outflow check valve are arranged side by side in the direction orthogonal to the drive shaft As a result, it is easy to reduce the size of the pump in the direction along the drive shaft, and it becomes easy to arrange a plurality of pumps side by side along the drive shaft.
In this case, when an O-ring that seals between the inner peripheral surface of the cylinder part and the outer peripheral surface of the plunger is applied, the shape of the O-ring in the state where no external force is applied corresponds to the cross-sectional shape of the plunger. It is preferable to use an oval shape that is long in the direction and flattened in a direction perpendicular to the direction. By fitting the longitudinal direction of the O-ring in accordance with the longitudinal direction of the plunger cross section, it is possible to prevent the O-ring from protruding unevenly from the outer peripheral surface of the plunger, and uniform sealing performance over the circumference of the plunger. Is secured.
When an O-ring that seals between the inner peripheral surface of the cylinder part and the outer peripheral surface of the plunger is applied, it is preferable to dispose a plurality of O-rings at different positions with respect to the forward / backward movement direction axis of the plunger. This prevents the tilting of the plunger with respect to the cylinder portion and maintains parallelism, thereby improving the smoothness and efficiency of the plunger's forward and backward movement, and the double O-ring is always uniformly distributed on the inner periphery of the cylinder portion. Adheres to the surface and improves sealing performance.

  In addition, since the valve chamber is almost unnecessary by forming the check valve from a flat plate, the internal volume of the cylinder portion and the valve chamber when the plunger is at the bottom dead center can be reduced. Even when a gas such as air is present, it is possible to reduce the influence of a decrease in pump efficiency. For this reason, even if the pump is started from the empty state, the lubricating oil can be sucked and discharged, and the work of manually filling the lubricating oil into the pump in advance can be made unnecessary. Efficiency can be improved.

In addition, in the case where the return spring of the plunger is provided, the structure in which the return spring is arranged outside the cylinder portion makes it easy to obtain a structure in which the cylinder internal volume is zero, and there is gas In this case, the reduction in pump efficiency can be further reduced.
Further, if the flat plate is made of spring steel, the durability is high and the pump is downsized.

Even if a leaf spring valve body is applied to only one of the inflow side check valve and the outflow side check valve, the effect of reducing the valve chamber can be obtained.
In this way, when applied to only one side, a leaf spring valve body is applied only to the inflow side check valve, and a valve body and a coil spring disposed downstream of the regulating body are applied as the outflow side check valve. It is preferable to do. Also in this case, since the valve body and the coil spring are on the downstream side of the regulating body, that is, outside the cylinder portion, the bottom dead center of the plunger is not raised. Further, the leaf spring valve body of the inflow side check valve is disposed inside the cylinder portion when bent, but the leaf spring valve body of the outflow side check valve is disposed outside the cylinder portion. Since the flow velocity changes drastically in the flow path where the cross-sectional area of the flow path is smaller than that of the cylinder, the repeated load accompanying the pump operation increases. On the other hand, it may be effective to increase the fatigue limit by applying a valve body supported by a coil spring. Further, when a leaf spring valve body is applied only to the inflow side check valve, the base body fixed to the pump body can constitute the regulating body provided with the above-described passage port. The flat plate which forms a body can be made into one sheet.

It is a perspective view of the oil supply pump of the sewing machine which is 1st Embodiment of invention. It is a top view of the oil supply pump of the sewing machine of 1st Embodiment. It is sectional drawing in alignment with the WW line in FIG. 2 of the oil pump of the sewing machine of 1st Embodiment. It is the perspective view which notched some oil supply pumps of the sewing machine of 1st Embodiment along the YZ plane. FIG. 3 is a perspective view illustrating two flat plates sandwiched between a pump main body and a base in the first embodiment so as not to overlap with each other according to the vertical order. It is an expanded sectional view which shows the structure of the non-return valve of 1st Embodiment, (A), (C) shows a valve open state, (B), (D) shows a valve obstruction | occlusion state. It is the perspective view which arranged and arranged the three flat plates clamped by the pump main body and foundation of 2nd Embodiment so that it might not overlap according to an up-down order. It is an expanded sectional view which shows the structure of each check valve of 2nd Embodiment, (A), (C) shows a valve open state, (B), (D) shows a valve obstruction | occlusion state. It is a disassembled perspective view of the oil pump of the sewing machine of 3rd Embodiment. It is sectional drawing about the plane containing the central axis of the two outflow ports of the oil pump of the sewing machine of 3rd Embodiment. It is sectional drawing about the plane containing the central axis of one inflow port and one outflow port of the oil pump of the sewing machine of 3rd Embodiment. It is sectional drawing which shows the oil pump of the conventional sewing machine.

(Outline of the embodiment)
Hereinafter, preferred embodiments for carrying out the present invention will be described with reference to the drawings. However, although various technically preferable limitations for implementing the present invention are given to the embodiments described below, the scope of the invention is not limited to the following embodiments and illustrated examples.
First, a first embodiment of the present invention will be described with reference to FIGS.
1 is a perspective view of an oil pump 10 for a sewing machine according to a first embodiment, FIG. 2 is a plan view of the first embodiment, FIG. 3 is a cross-sectional view taken along line WW in FIG. 2, and FIG. It is the perspective view which notched the part along the Y direction. FIG. 5 is a perspective view showing two flat plates sandwiched between the pump main body and the base in the first embodiment so as not to overlap each other according to the upper and lower order, and FIG. 6 is the reverse of the first embodiment. It is an expanded sectional view which shows the structure of a stop valve. In addition, although the lower shaft 1 and the eccentric cam 21 which will be described later are shown in FIG. 3, they are omitted in other drawings.

As shown in FIG. 1, the oil pump 10 for the sewing machine is installed below a lower shaft 1 that is one of drive shafts that rotate by driving a sewing machine motor (not shown). In addition, although the oil pump 10 illustrated here is a duplex type in which two main parts of the pump structure are provided, it goes without saying that the main part may be one. In addition, one thing is provided with only one each of the cylinder part 41, the plunger 30, the inflow side check valve 50, the outflow side check valve 60, etc. which are mentioned later.
One of the dual-type oil pumps 10 is used to return the lubricating oil collected in the oil pan of the sewing machine to the oil tank, and the other is used to send the lubricating oil from the oil tank to each mechanism that supplies the lubricating oil. Used.
In addition, since each part (the cylinder part 41, the plunger 30, the inflow side check valve 50, the outflow side check valve 60 etc. which are mentioned later) which comprises the principal part of a dual-type pump is the same structure, it is the same. The configuration will be described with the same reference numerals.

The oil pump 10 moves forward and backward (up and down) by means of a motion converting mechanism 20 for converting the torque of the lower shaft 1 into a linear motion reciprocating motion and two eccentric cams 21 (described later) of the motion converting mechanism 20. Two plungers 30 and pump bodies 40 in which the respective plungers 30 are inserted and two cylinder parts 41 are formed so as to be movable up and down are provided in each cylinder part 41 and flow into each cylinder part 41. An inflow check valve 50 that allows only the flow of the lubricating oil in the direction to flow, and an outflow side check valve that is provided in each cylinder portion 41 and allows only the flow of the lubricating oil in the direction that flows out from each cylinder portion 41. A valve 60 and a base 70 on which an inflow port 75 and an outflow port 76 of lubricating oil for each cylinder part 41 are formed are provided.
Hereinafter, each part will be described.
In the following description, the advancing / retreating direction of the plunger 30 described above is the vertical direction or the Z-axis direction, and the direction parallel to the lower shaft 1 on the plane orthogonal to the Z-axis direction is the Y-axis direction, and the lower shaft 1 The direction orthogonal to is the X-axis direction.

(Pump body)
The pump body 40 is formed of a rectangular block in a plan view, and is provided with two cylinder portions 41 formed so as to penetrate along the Z-axis direction. The two cylinder portions 41 are formed in an oval shape in plan view. The plane in plan view is the XY plane.
The two cylinder parts 41 are provided side by side along the Y-axis direction. In each cylinder part 41, the longitudinal direction of an ellipse having a cross-sectional shape is directed to the X-axis direction.
Also, a long hole-like mounting hole 42 penetrating along the Z-axis direction is formed at one end of the pump body 40 in the X-axis direction, and is attached to the sewing machine frame by a mounting screw on the lower side of the lower shaft 1. It comes to be fixedly equipped.

  In addition, a rectangular base 70 in plan view having a small width in the Y-axis direction and a small width in the X-axis direction is fixed by four screws 71 to 74 below the pump body 40. Further, two flat plates 81 and 83 for forming two inflow check valves 50 and two outflow check valves 60 are interposed between the pump body 40 and the base 70, These flat plates 81 and 83 are clamped by fastening four screws 71 to 74. These flat plates 81 and 83 close the lower openings of the cylinder portions 41 of the pump main body 40 described above and serve as the bottom plate of the cylinder portion 41.

(Motion conversion mechanism)
The motion conversion mechanism 20 includes two circular eccentric cams 21 fixedly mounted on the lower shaft 1 in a state of being arranged close to each other, and two plungers 30 that are in contact with the eccentric cams 21 and pressed downward. Two return springs 22 for pushing back and an interlocking plate 23 for transmitting the pressing force of each return spring 22 to two plungers 30 at the same time are provided.
Each eccentric cam 21 is an outer peripheral cam that presses each plunger 30 downward in accordance with the rotation cycle of the lower shaft 1 by bringing the outer periphery thereof into contact with the upper end surface of each plunger 30. These eccentric cams 21 are fixed to the lower shaft 1 in a state where the phases are matched.
The eccentric cam 21 is not limited to a circular shape, and may have any shape that can press the plunger 30 by the rotation of the lower shaft 1, or may have a shape that can be pressed a plurality of times for one rotation of the lower shaft 1. A triangular eccentric cam 102 shown in FIG.

The interlocking plate 23 is formed with two substantially U-shaped cutouts 23a, and each cutout 23a is a fitting formed in the vicinity of the upper end of each plunger 30 at both ends in the longitudinal direction. The grooves 31 are fitted and fixed to each other. As a result, the interlocking plate 23 and the two plungers 30 move up and down together.
Further, two bosses 23b projecting downward are formed at both ends in the X-axis direction on the lower surface of the interlocking plate 23, and each return spring 22 is fitted and held.
Each return spring 22 is inserted between the lower surface of the interlocking plate 23 and the upper surface of a base 70 described later, and presses the interlocking plate 23 and the two plungers 30 connected thereto upward.
Although not shown, a circular groove in which each return spring 22 is accommodated is formed on the upper surface side of the base 70.
The two screws 72 and 73 described above are fixedly equipped with flange-shaped stoppers 72a and 73a on the outer periphery of the head. For this reason, even when the oil pump 10 is removed from the lower side of the lower shaft 1, the lower surfaces of the retaining members 72 a and 73 a abut against the upper surface of the interlocking plate 23, so that each plunger 30 is pressed by the return spring 22. It is designed not to jump out. Even if the plunger 30 is moved to the highest position by the eccentric cam 21, these stoppers 72a and 73a are connected to the stoppers 72a and 73a and the interlocking plate 23 (the interlocking plate 23 at the highest position in FIG. The height is set so that a predetermined amount of gap h is formed between the upper surface and the upper surface.

(Plunger)
As described above, each plunger 30 has an oval shape in the same plan view as the cylinder portion 41, and is uniformly formed in the same shape along the Z-axis direction. Each plunger 30 is fitted in the cylinder portion 41 and can reciprocate along the Z-axis direction in the cylinder portion 41 with its upper portion protruding outward. Moreover, both the upper end surface and the lower end surface are formed smoothly. In the vicinity of the upper end surface, the fitting groove 31 is formed as described above, and is pressed upward by the return springs 22 via the interlocking plate 23.
A ring groove 32 is formed on the outer peripheral surface in the vicinity of the lower end surface of each plunger 30, and an O-ring 33 is attached. The O-ring 33 seals the outer peripheral surface of the plunger 30 and the inner wall of the cylinder portion 41, and a sealed region is formed in the cylinder portion 41 and below the plunger 30. Then, as the plunger 30 moves up and down, the lubricating oil flows into or out of this sealed region through the inflow side check valve 50 and the outflow side check valve 60.

As described above, the outer periphery of the eccentric cam 21 is in contact with the upper end surface of the plunger 30. When the downward displacement of the eccentric cam 21 is the smallest, the plunger 30 is at the highest position (the highest position), and below the eccentric cam 21. When the displacement is the largest, it is the lowest position (the lowest lowered position).
When each plunger 30 is located at the lowest lowered position, the lower end surface thereof is substantially in contact with the upper surface of the flat plate 81 serving as the bottom of the cylinder portion 41, and the volume of the cylinder portion 41 (the volume of the sealed region) is substantially zero. Designed to be

Further, an inflow check valve 50 and an outflow check valve 60 are provided on the lower side of each plunger 30 so as to face the lower end surface thereof, and further, through the inflow check valve 50. The sealed region is connected to the lubricant inlet 75, and the sealed region is connected to the lubricant outlet 76 via the outlet check valve 60.
The inflow side check valve 50 is located on one end side in the longitudinal direction on the lower end surface of the plunger 30, and the outflow side check valve 60 is located on the other end side. Further, since the plunger 30 is formed in an oval shape, the main configuration of the pump can be reduced in size in the direction orthogonal to the oval (Y-axis direction), for example, aligned along the lower shaft 1. A plurality of pumps can be provided.

(Base)
An inflow port 75 is vertically formed at each position of the base 70 that faces one end of the bottom surface of each plunger 30, and a flow at each position that opposes the other end of the bottom surface of each plunger 30. An outlet 76 is formed so as to penetrate vertically.
In addition, female threads are formed on the inner surfaces of the inflow ports 75 and the outflow ports 76, and a hose joint 77 for connecting the inflow hose and a hose joint 78 for connecting the outflow hose are respectively screwed.

(Inflow check valve and outflow check valve)
FIG. 5 is a perspective view illustrating two flat plates 81 and 83 sandwiched between the pump main body 40 and the base 70 according to an upper and lower order, and FIG. 6 is an inflow check valve 50 and an outflow check valve 60. It is an expanded sectional view which shows the structure.

Here, the basic structure of the inflow side check valve 50 will be described as an example with reference to FIGS. The flat plates 81 and 83 are overlapped so that the check valve 50 is aligned along the direction allowing the flow. In addition, each flat plate 81 and 83 is the same size and the same shape as the upper surface of the base 70 mentioned above.
In order to form the cantilever-like valve body 51 on the flat plate 81 which is the most downstream side in the permissible flow direction of the inflow side check valve 50, a slit having a shape (for example, C-shape) along the outer shape of the valve body 51 Is formed. Since the valve body 51 has a cantilever structure, the free end side thereof can be bent up and down.

  The flat plate 83 adjacent to the upstream side in the flow-permissible direction with respect to the flat plate 81 is penetrated by a passage port 53 having a size capable of completely closing the valve body 51 at a position overlapping the valve body 51. Is formed. The size of the passage port 53 has a function as a throttle hole that influences the passage amount of the lubricating oil passing through the inflow side check valve 50. A portion of the flat plate 83 around the passage port 53 functions as a regulating body (the passage port 53 is also referred to as a regulating body).

  With this structure, since the passage port 53 is smaller than the valve body 51, the valve body 51 is regulated so as not to bend toward the passage port 53 side (upstream side in the flow allowable direction). As a result, when the lubricating oil flows in the inflow direction IN side (flow allowable direction, when the internal pressure in the sealed region of the cylinder portion 41 is low), the valve body 51 bends upward and opens to allow the flow. Allowed (state shown in FIG. 6A). Further, the flow rate at that time is limited to a flow rate corresponding to the inner diameter of the passage port 53. Further, when the lubricating oil is about to flow in the outflow direction OUT side (when the internal pressure in the sealed region of the cylinder portion 41 becomes high), the valve body 51 receives pressure on the passage port 53 side, but in that direction The bending is prevented, the passage port 53 is closed, and the flow is blocked (the state shown in FIG. 6B).

  In this way, the inflow side check valve 50 is configured by the valve body 51 formed on the flat plate 81 and the passage port 53 (strictly, a restricting body made of the surrounding area) formed on the flat plate 83.

Further, since the outflow check valve 60 is opposite in flow direction to the inflow check valve 50, the valve body 61 formed in the flat plate 83 and the passage port 63 formed in the flat plate 83 (strictly speaking, the periphery thereof) (Regulatory body consisting of the part). And the valve body 61 is the same structure as the valve body 51 mentioned above, and the passage port 63 (it is also called a control body) is the same structure as the passage port 53 (control body) mentioned above.
With this configuration, when the lubricating oil flows in the outflow direction check valve 60 in the outflow direction OUT side (when the internal pressure in the sealed region of the cylinder portion 41 is increased), the valve body 61 is To be opened and allowed to flow (state shown in FIG. 6C). Further, when the lubricating oil is about to flow in the inflow direction IN side (when the internal pressure in the sealed region of the cylinder portion 41 becomes low), the valve body 61 receives pressure from the outside on the passage port 63 side. Is prevented from being bent, the passage port 63 is closed, and the flow is blocked (the state shown in FIG. 6D).

The flat plate 81 and the flat plate 83 are formed with mounting holes 64a, 64b, 64c, and 64d for passing through screws 71, 72, 73, and 74 that fix the pump main body 40 and the base 70, respectively. The flat plate 81 and the flat plate 83 are formed with holes 65a and 65b through which the return spring 22 passes. In the flat plate 81, the set of the valve body 51 and the passage port 63, the set of the mounting holes 64a and 64c and the mounting holes 64b and 64d, and the set of the holes 65a and 65b with respect to the center line y1 in the left-right direction It is formed in a symmetrical position. Further, the flat plate 83 has a pair of the valve body 61 and the passage port 53, a pair of the mounting holes 64b and 64d and the mounting holes 64a and 64c, and a pair of the holes 65b and 65a with respect to the center line y1 in the left-right direction. It is formed in a symmetrical position.
For this reason, the flat plate 81 and the flat plate 83 are the same structure, and the only difference is that the front and back of the direction in which they are arranged are opposite to each other. In addition, about the valve body and passage which were each formed, in order to show clearly the response | compatibility with the inflow side check valve 50 and the outflow side check valve 60, a different code | symbol is attached | subjected.
Two adjacent flat plates in which a valve body and a passage port (regulator) are formed are overlapped so that the valve body and the passage port face each other, so that the adjacent inflow check valve 50 and the outflow side reverse A stop valve 60 can be formed. In this way, it is possible to reduce manufacturing costs by unifying parts.
The flat plate 81 and the flat plate 83 are formed of a thin spring steel material having a thickness of 0.05 mm, and a stainless steel spring steel material is also preferable. Further, the flat plate 81 and the flat plate 83 may be formed as a plate material made of fiber reinforced rubber.

(Operation of sewing machine oil pump)
When the sewing machine motor is driven and the lower shaft 1 rotates, the oil supply pump 10 having the above configuration also rotates the eccentric cam 21 to periodically push the plunger 30 downward. The plunger 30 moves up and down in synchronization with the rotational speed of the lower shaft 1 by the action of the return spring 22 and the eccentric cam 21.
As a result, when the plunger 30 is raised, the inside of the sealed region is depressurized, the inflow check valve 50 is allowed to flow in the lubricating oil, and the lubricating oil is sucked into the inside. On the other hand, at this time, the outflow check valve 60 is closed.
When the plunger 30 is lowered, the pressure in the sealed region is increased, the outflow check valve 60 allows the outflow of the lubricating oil, and the lubricating oil is discharged to the outside. On the other hand, at this time, the inflow side check valve 50 is closed.
In this way, the plunger 30 repeatedly moves up and down, so that the lubricating oil is intermittently sucked from the inflow port 75 through the hose joint 77 for connecting the inflow hose and from the outflow port 76 for connecting the outflow hose. The lubricating oil is completely delivered through the hose joint 78.

Next, a second embodiment of the present invention will be described based on FIGS.
In the first embodiment, the inflow side check valve 50 and the outflow side check valve 60 are constituted by two flat plates 81 and 83. On the other hand, 2nd Embodiment is comprised by the three flat plates 81,82,83. The intermediate flat plate 82 is formed with throttle holes 52 and 62 so as to face the passage holes 53 and 63. The throttle holes 52 and 62 are smaller than the passage holes 53 and 63 and have a function of arbitrarily and easily adjusting the supply amount of the pump. Further, as shown in FIG. 8, when the valve bodies 51 and 61 are in a horizontal straight line, the valve bodies 51 and 61 are formed so as to be able to completely close the throttle holes 52 and 62.

(Effect of sewing machine oil pump)
In the oil supply pump 10, the inflow side check valve 50 and the outflow side check valve 60 are formed by two or three flat plates, so that the check valves 50, 60 are made thin, and the valve chamber is substantially made up. Since it is not necessary, it is possible to realize a significant downsizing of the entire pump.
Further, since the valve body and the regulating body are formed by processing the flat plate, it is possible to facilitate processing and manufacturing.
In addition, since the check chambers 50 and 60 are formed of flat plates, the valve chamber is almost unnecessary, so that the internal volume of the cylinder portion 41 and the valve chamber when the plunger is at the bottom dead center is reduced. Even when a gas such as air is present inside the cylinder, it is possible to reduce the influence of a decrease in pump efficiency. For this reason, even if the pump is started from the empty state, the lubricating oil can be sucked and discharged, and the work of manually filling the lubricating oil into the pump in advance can be made unnecessary. Efficiency can be improved.

In particular, since the return spring 22 of the plunger 30 is disposed outside the cylinder portion 41 and the plunger 30 is lowered to a position in contact with the flat plate 81, the internal volume of the sealed region of the cylinder portion 41 can be made substantially zero. Therefore, it is possible to further reduce the decrease in pump efficiency when there is a gas such as air inside the cylinder, the pump can be started more smoothly from the empty state, and the work efficiency can be further improved. It becomes possible to plan.

  Moreover, since the oil supply pump 10 inserts the flat plate 82 in which the throttle holes 52 and 62 are provided between the two flat plates 81 and 83, the supply amount of the pump can be arbitrarily and easily adjusted. .

Next, a third embodiment of the present invention will be described with reference to FIGS.
In the first embodiment, the inflow side check valve 50 and the outflow side check valve 60 are constituted by two flat plates 81 and 83. On the other hand, the third embodiment is different in that only one flat plate 81 is applied, and the outflow check valve includes a valve body 91 and a coil spring 92 that are independent from the flat plate 81, and the base 70A and the outflow are further different. The shape of the hose joint 78A for connecting the hose is different. In the third embodiment, two ring grooves 32A and 32B are formed on the outer peripheral surface of the plunger 30A, and two O-rings 33A and 33B are mounted. The following description will focus on the parts different from those of the first embodiment. Other forms are the same as in the first embodiment.

First, in the third embodiment, one flat plate 81 made of a spring steel plate is sandwiched between the pump body 40 and the base 70A. The structure of the flat plate 81 is the same as that of the first embodiment, and the valve body 51 constitutes the valve body of the inflow side check valve, and the peripheral portion of the passage port 63 of the valve body 51 serves as the regulating body of the outflow side check valve. Constitute.
A hose joint 80 for connecting an inflow hose is integrally formed on the base 70A in order to secure an inflow path. The restricting body of the inflow side check valve is constituted by the base 70A because the inner diameter of the inflow port 75A of the base 70A (at least the inner diameter of the end in contact with the flat plate 81) is smaller than the diameter of the valve body 51. The base 70A has two oval cylinder holes (cylinder portions) 41 and 41 formed in parallel, and mounting holes 40A and 40A for the return spring 22 are formed at both ends thereof.

A coil spring holding portion 93 is formed in the hollow portion of the connection end portion of the hose joint 78A for connecting the outflow hose to the base 70A. One end of the coil spring 92 is inserted into the coil spring holding portion 93 so that the coil spring 92 is held. The coil spring holding portion 93 is a flow path having an inner diameter in which the outer diameter of the coil spring 92 is accommodated, and the flow path downstream from the coil spring holding section 93 is formed to have an inner diameter smaller than the outer diameter of the coil spring 92, thereby Is a structure to be locked.
A valve body 91 is fixed to the other end of the coil spring 92. The valve body 91 is sufficient if it is made of, for example, the same material as the flat plate 81, a resin plate, or the like and closes the passage port 63.
The coil spring 92 presses the valve body 91 against the restricting body (a portion around the passage opening 63) to close the passage opening 63, and when the plunger 30A is lowered, the valve body 91 is pushed by hydraulic pressure, and the coil spring 92 is contracted and deformed. Thus, a mechanism is formed in which the passage port 63 is opened by separating the valve body 91 from the regulating body (a portion around the passage port 63).

According to the third embodiment configured as described above, the inflow side check valve functions to open and close as in the first embodiment.
When the valve is opened, the valve body 51 of the inflow side check valve bends toward the cylinder part 41 side. When the lubricating oil flows into the cylinder portion 41, which is a space having a larger flow path cross-sectional area than the inlet 75A, the flow velocity is reduced. On the other hand, when it flows out to the outflow port 76 which is a space having a smaller channel cross-sectional area than the cylinder part 41, the flow velocity increases.
From the above, the repeated load accompanying the pump operation applied to the valve body 61 of the first and second embodiments is larger than that of the valve body 51, and it is necessary to design in consideration of this point. In the first and second embodiments, the material and thickness of the flat plate 83 can be selected to achieve sufficient durability. However, in order to improve the durability at a lower price, Three embodiments are preferred.
In particular, in the third embodiment, the valve body 91 is supported in a movable state by the elasticity of the coil spring 92. Therefore, it is easy to achieve high durability that can withstand repeated loads at the discharge portion.
A standard product can be applied as the coil spring 92, and the valve body 91 can also be constituted by a part where the flat plate 81 is removed.
According to the third embodiment, since only one flat plate 81 is sandwiched between the pump body 40 and the base 70A, the oil supply pump can be further reduced in size compared to the first and second embodiments.

  Two ring grooves 32A and 32B are provided around the outer peripheral surface of the plunger 30A. The O-ring 33A is fitted into the ring groove 32A, the O-ring 33B is fitted into the ring groove 32B, and the two O-rings 33A and 33B are attached to the plunger 30A. The two ring grooves 32A and 32B are provided at different positions with respect to the forward / backward movement direction axis of the plunger 30A. Accordingly, the two O-rings 33A and 33B are arranged at different positions with respect to the forward / backward movement direction axis of the plunger 0A. The O-rings 33A and 33B are thus provided on the outer periphery of the plunger 30A and seal between the inner peripheral surface of the cylinder portion 41 and the outer peripheral surface of the plunger 30A. Therefore, the O-rings 33A and 33B are in contact with the inner peripheral surface of the cylinder portion 41, and the plunger 30A is supported by the cylinder portion 41 with the O-rings 33A and 33B as fulcrums. Since the two O-rings 33A and 33B are arranged at different positions with respect to the forward / backward movement direction axis of the plunger 30A, the plunger 30A is prevented from being tilted with respect to the cylinder part 41 and parallel to the axis of the plunger 30A and the axis of the cylinder part 41. The degree can be maintained, and the smooth and efficient forward / backward movement of the plunger 30A can be executed. The double O-rings 33A and 33B which are separated from each other in the vertical direction are always in close contact with the inner peripheral surface of the cylinder portion 41, and the sealing performance can be ensured.

Similar to the first and second embodiments, the cross-sectional shape of the plunger 30A viewed from the advancing / retreating direction is elongated along the direction orthogonal to the drive shaft.
Corresponding to the flat and long cross-sectional shape of the plunger 30A, the O-rings 33A and 33B are also formed in a flat and long shape as shown in FIG.
In other words, the O-rings 33A and 33B have an oval shape in a state in which no external force is applied, which is long in one direction and flattened in a direction perpendicular to the cross-sectional shape of the plunger 30A.
When a circular O-ring is externally fitted to the plunger 30A having a flat and long cross-sectional shape, the O-ring expands and deforms in the major axis direction of the plunger 30A, and from the outer circumferential surface of the plunger 30A in the minor axis direction than the major axis direction. It may be easy to protrude. In this case, there is an inconvenience that it is difficult to insert the plunger 30 </ b> A equipped with the O-ring into the cylinder part 41.
In the third embodiment, the O-rings 33A and 33B are fitted into the outer circumference of the plunger 30A by fitting the longitudinal direction of the oval O-rings 33A and 33B in accordance with the longitudinal direction of the cross section of the plunger 30A in a state where no external force is applied. Non-uniform protrusion from the surface is prevented, and a uniform sealing property is secured over the circumference of the plunger 30A. Further, the plunger 30A to which the O-rings 33A and 33B are attached can be smoothly inserted into the cylinder part 41.

It should be noted that both or one of the upper and lower double seal structures by the two O-rings 33A and 33B and the oval shape of the O-ring 33A (33B) employed in the third embodiment described above are used as the first or second. It goes without saying that the effects can also be obtained by implementing the embodiment applied to the embodiment.
As described above, in the third embodiment, in order to improve durability, the inflow side check valve is composed of the plate-shaped valve body 51 and the regulating body (inlet 75A of the base 70A), and the outflow side reverse The stop valve is composed of a valve body 91 and a regulating body (a portion around the passage port 63). However, if the normal durability performance is sufficient, the first embodiment and the second embodiment are preferable.
From these embodiments, the oil pump of the sewing machine according to the present invention moves forward and backward by the motion conversion mechanism 20 that converts the torque of the drive shaft that rotates using the sewing machine motor as a drive source, and the motion conversion mechanism. An inflow side for supporting only the plunger 30, the pump main body 40 including the cylinder portion 41 that supports the plunger 30 so as to be movable back and forth, and the flow of the lubricating oil only in the direction of flowing into the cylinder portion while communicating with the cylinder portion 41. A check valve 50 and an outflow side check valve 60 that communicates with the cylinder portion and allows only the flow of the lubricating oil in the direction of flowing out from the cylinder portion.
Each of the inflow side check valve and the outflow side check valve is provided with valve bodies 51 and 91 and lubricating oil passage ports 75A and 76 that can be closed by the valve body on the upstream side in the flow allowable direction of the valve body. One of the inflow side check valve and the outflow side check valve as the valve body 51 flows by elastically bending toward the downstream side in the permitted flow direction of the lubricating oil. What is necessary is just to provide the plate-shaped valve body by which a path | route is opened.
In addition, the outflow check valve of the third embodiment includes a valve body 91 and a coil spring 92 arranged on the downstream side of the restricting body of the outflow check valve (the peripheral portion of the passage port 63). Then, the coil spring 93 presses the valve body 91 against the regulating body to close the passage port 63 provided in the regulating body, and the valve spring 91 is moved downstream from the regulating body (OUT side) by contraction deformation of the coil spring 92. The passage port 63 is opened by making it diverge toward.
Further, in the third embodiment, the valve body 51 of the inflow side check valve and the regulating body of the outflow side check valve are formed on the same flat plate 81, and the flat plate 81 is overlapped with the pump main body 40. is doing.
In the third embodiment, a base 70 </ b> A is provided below the pump body 40 and fixed to the pump body 40. In the pump main body 40, the cylinder portion 41 is formed so that the bottom thereof is open, and the flat plate 81 is sandwiched between the pump main body 40 and the base, thereby closing the open bottom. Further, the plunger 30 </ b> A is moved by the motion conversion mechanism 20 to the extent that the plunger 30 </ b> A contacts the flat plate 81. Furthermore, the regulating body of the inflow side check valve is constituted by a base 70A.

(Other)
The motion converting mechanism is exemplified by the outer peripheral cam, but is not limited thereto, and may be a groove cam. In that case, since the plunger 30 is connected so as to move up and down in accordance with the groove of the cam, the return spring 22 is unnecessary. Further, the motion conversion mechanism is not limited to the cam mechanism but may be a crank mechanism. For example, the other end of a connecting rod having an eccentric cam fixedly mounted on the lower shaft 1 may be connected to the plunger 30 and the plunger 30 may be moved up and down in synchronization with the rotation of the lower shaft 1. In this case, the return spring 22 is not necessary.
Further, although one eccentric cam 21 constituting the motion converting mechanism is provided for each of the two plungers 30, it can be easily replaced with one eccentric cam 21 that contacts the two plungers.
In the above-described embodiment, two plungers are arranged in the oil supply pump to efficiently obtain a predetermined oil supply amount. However, it is easily conceivable to supply oil with one plunger.

1 Lower shaft (drive shaft)
20 Action Conversion Mechanism 21 Eccentric Cam 22 Return Spring 30 Plunger 40 Pump Main Body 41 Cylinder Unit 50 Inflow Side Check Valve 51 Valve Body 52 Restriction Hole 53 Passing Port (Regulator)
60 Outflow side check valve 61 Valve body 62 Restriction hole 63 Passage port (regulator)
81, 82, 83 Flat plate 91 Valve body 92 Coil spring

Claims (13)

An operation conversion mechanism that converts torque of a drive shaft that rotates using a sewing machine motor as a drive source to linear motion reciprocation;
A plunger that moves forward and backward by the motion conversion mechanism;
A pump body that supports the plunger so as to move forward and backward, and includes a cylinder portion;
An inflow check valve that communicates with the cylinder portion and allows only the flow of lubricating oil in the direction of flowing into the cylinder portion;
In an oil supply pump of a sewing machine provided with an outflow check valve that communicates with the cylinder portion and allows only the flow of lubricating oil in the direction of flowing out of the cylinder portion,
The inflow side check valve and the outflow side check valve are both a valve body and a regulating body provided with a passage for lubricating oil that can be closed by the valve body on the upstream side of the valve body in the flow allowable direction. With
One of the inflow check valve and the outflow check valve is a plate-shaped member that opens as a valve body by elastically deflecting toward the downstream side in the allowable flow direction of the lubricating oil as the valve body. A sewing machine oil pump comprising a valve body. Each of the inflow side check valve and the outflow side check valve includes the plate-shaped valve body,
The valve body of the inflow side check valve and the restriction body of the outflow side check valve are formed on the same flat plate, and the restriction body of the inflow side check valve and the valve body of the outflow side check valve are the same. Formed on the other flat plate,
The oil pump for a sewing machine according to claim 1, wherein the two flat plates are provided so as to overlap with the pump body.   The two flat plates have the same shape and structure, and one flat plate valve body and the other flat plate restricting body face each other, and one flat plate restricting body and the other flat plate valve body face each other. The oil pump for a sewing machine according to claim 2, wherein the oil pump is attached to the pump body so as to overlap with each other. A base disposed below the pump body and fixed to the pump body;
In the pump body, the cylinder part is formed so that the bottom part is opened, and the two flat plates are sandwiched between the pump body and the base, thereby closing the opened bottom part,
4. The oil supply pump for a sewing machine according to claim 2, wherein the plunger is moved by the motion converting mechanism to such an extent that the plunger comes into contact with the flat plate on the pump body side.   A flat plate provided with a throttle hole for adjusting the flow rate of lubricating oil is disposed between the two flat plates so as to be disposed between the individual valve bodies and the individual regulating bodies. Item 5. The sewing machine oil pump according to any one of Items 2 to 4. The inflow side check valve includes the plate-like valve body,
The outflow side check valve includes a valve body and a coil spring disposed on the downstream side of the regulating body of the outflow side check valve,
The coil spring presses the valve body against the regulating body to close the passage port provided in the regulating body, and the passage is performed by causing the valve body to be separated from the regulating body by contraction deformation of the coil spring. 2. The sewing machine oil pump according to claim 1, wherein the mouth is opened.   The valve body of the inflow side check valve and the restricting body of the outflow side check valve are formed on the same flat plate, and the flat plate is overlapped with the pump body. Item 7. A sewing machine oil pump according to Item 6. A base disposed below the pump body and fixed to the pump body;
In the pump body, the cylinder part is formed so that the bottom part is opened, and the flat plate is sandwiched between the pump body and the base, thereby closing the opened bottom part,
The plunger is moved to the extent that it comes into contact with the flat plate by the motion conversion mechanism,
The oil supply pump for a sewing machine according to claim 7, wherein the restricting body of the inflow side check valve is constituted by the base.   The oil pump for a sewing machine according to any one of claims 2 to 4 and 7 to 8, wherein the flat plate is made of a spring steel material. The motion conversion mechanism applies a moving force in only one of the forward and backward movement directions to the plunger,
The plunger is provided with a return spring that imparts a moving force in the remaining direction of the forward / backward movement direction,
The oil pump for a sewing machine according to any one of claims 1 to 9, wherein the return spring is disposed outside the cylinder portion. The motion conversion mechanism is an eccentric cam fixed to the drive shaft.
While arranging the inflow side check valve and the outflow side check valve side by side in a direction orthogonal to the drive shaft,
11. The oil pump for a sewing machine according to claim 1, wherein a cross-sectional shape of the plunger viewed from the advancing / retreating direction is elongated along a direction orthogonal to the drive shaft. Provided on the outer periphery of the plunger, comprising an O-ring for sealing between the inner peripheral surface of the cylinder part and the outer peripheral surface of the plunger;
The shape of the O-ring in a state in which no external force is applied is an oval shape that is long in one direction and flattened in a direction perpendicular to the cross-sectional shape of the plunger. Sewing machine oil pump. A plurality of O-rings provided on the outer periphery of the plunger and sealing between the inner peripheral surface of the cylinder part and the outer peripheral surface of the plunger;
The oil pump for a sewing machine according to any one of claims 1 to 12, wherein the plurality of O-rings are arranged at different positions with respect to a forward / backward movement direction axis of the plunger.

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