JP2015158151A - Reciprocating drive pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reciprocating drive pump which simplifies a coolant feed passage and improves the assemblability and maintainability.SOLUTION: A reciprocating drive pump 1 includes: a cylinder having a cylinder body part 30 and a valve box 60; a reciprocating body 20; a suction port 61 and a discharge port 62; a suction passage 61a which allows the suction port 61 and a cylinder chamber 30a to communicate with each other; and liquid supply means 3 which supplies a liquid to the cylinder chamber 30a through the suction passage 61a. The reciprocating drive pump 1 includes: a gland packing 32 which seals a space between the cylinder body part 30 and the reciprocating body 20; and a cooling device 50 which cools the gland packing 32. The cooling device 50 includes a coolant feed passage 54 which branches from a branch point 51 of the suction passage 61a to communicate with the gland packing 32. The liquid supply means 3 feeds the liquid supplied to the suction port 61 from the coolant feed passage 54 to the gland packing 32 as a coolant.

Description

  The present invention relates to a reciprocating drive pump, and more particularly to a reciprocating drive pump provided with a cooling device for cooling a gland packing.

  A reciprocating pump (piston pump) is suitable for obtaining a high-pressure liquid (for example, water). For this reason, piston pumps are widely used in suspensions, cleaning devices for machine parts or deburring devices, cleaning devices for chemical devices, and the like. Devices that use high-pressure liquid often have many pipes and valves. For this reason, piping and valves may be arranged in a complicated manner. In particular, in the connection portion of the high-pressure pipe, high-pressure water may be ejected due to deterioration of the pipe and the pipe connection portion. This high-pressure water will cause serious damage if it hits the human body. For this reason, the high pressure water piping is provided with a safety cover, chain fixing and other safety measures.

  Conventionally, a piston pump is provided with a gland packing between a reciprocating body (plunger or piston) and a cylinder. The gland packing generates heat and wears as the reciprocating body moves back and forth. As the wear of the gland packing progresses, the liquid compressed by the reciprocating motion of the reciprocating body leaks and does not reach a predetermined pressure. For this reason, the gland packing is periodically replaced. In order to extend the life of the gland packing, a coolant is circulated through the gland packing, the gland packing is cooled by this coolant, and the sliding portion between the gland packing and the reciprocating body is lubricated ( For example, see Patent Document 1).

  In the piston pump described in Patent Document 1, a liquid as a cooling liquid is pumped to a high-pressure seal (corresponding to a gland packing) disposed between a reciprocating body and a cylinder by a pump that supplies liquid to the cylinder. A cooling device has been proposed.

Japanese Utility Model Publication No. 6-43277 (Claim 1, FIG. 1)

However, in the piston pump of Patent Document 1, the suction path to the piston pump and the piping of the coolant are branched from the pressure feed pump that supplies the liquid to the piston pump via the distributor. For this reason, when performing maintenance on the cylinder, gland packing, etc., it is necessary to separate the suction passage from the pumping pump to the piston pump and the coolant piping, disassemble the piston pump after removing the cooling device. there were. Piston pumps installed in cleaning equipment, etc. have complicated piping.To disassemble and connect the piping, it is necessary to check the piping to be constructed, manage the torque when connecting the piping, remove safety measures, and reconstruct the piping. It was necessary. For this reason, disassembling and reassembling the pipes are operations that are not directly related to the maintenance of the piston pump, but are very time-consuming operations.
In addition, if a coolant distribution mechanism and a flow rate adjustment mechanism are provided outside the piston pump, the number of piping around the piston pump increases, the piping design and construction is complicated, and the degree of freedom in piston pump layout is limited. There was a problem.

  In view of the above-described problems, an object of the present invention is to provide a reciprocating drive pump that simplifies liquid piping and a cooling liquid feeding path, improves assembly, and is easy to maintain.

  The present invention provides a cylinder having a cylinder body portion having a cylindrical shape and a valve box fixed to a tip portion of the cylinder body portion, a reciprocating body disposed in the cylinder body portion, A suction port and a discharge port arranged; a suction channel communicating from the suction port to the cylinder chamber; a liquid supply means for supplying a liquid from the suction port to the cylinder chamber through the suction channel; A gland packing that seals a gap between the cylinder main body and the reciprocating body, and a cooling device that cools the gland packing, and the cooling device branches off from a branch point of the suction flow path. A cooling liquid supply path communicating with the packing, and the liquid supply means supplies the liquid supplied to the suction port as a cooling liquid from the cooling liquid supply path to the gland packing. To liquid, characterized by.

  According to the present invention, the coolant supply path that branches from the branch point of the suction flow path and communicates with the gland packing is provided, so that the start point and end point of the liquid supply path for cooling the gland packing are Therefore, it is possible to attach and detach the cylinder together with the cylinder and the coolant supply path. For this reason, maintainability, such as a cylinder and a gland packing, can be improved.

  In addition, since the coolant flow path of the gland packing is branched from the branch point of the suction flow path, there is no need to pipe and connect from an external device such as a pressure feed pump that supplies liquid. The pipes to be connected may be only the suction pipe for sucking liquid and the discharge pipe for discharging. For this reason, the reciprocating drive pump according to the present invention can simplify the liquid piping, reduce the number of parts, and improve the assembly and maintenance.

  In the present invention, the valve box preferably includes the suction port, the discharge port, and a branch point of the suction flow path.

  According to the present invention, since the valve box is provided with the suction port, the discharge port, and the branch point, piping can be concentrated in the valve box, so the liquid piping is simplified and the number of parts is reduced. As a result, the assembling property and the maintenance property can be improved.

  In the present invention, it is desirable that the cooling liquid supply path has an opening of a liquid supply path that opens to an outer peripheral portion of the cylinder, and a flow rate adjusting means is disposed in the opening of the liquid supply path.

  According to the present invention, the flow rate adjusting means is firmly fixed to the cylinder by disposing the flow rate adjusting means by disposing the flow rate adjusting means at the opening portion of the liquid feed path that opens to the outer peripheral portion of the cylinder. Since operations and the like can be easily performed from the outside, assembly and maintenance can be improved.

  In the present invention, the coolant flow path extends through the cylinder main body from the outer peripheral portion toward the inner peripheral portion, and extends through the cylinder main body in the axial direction to the through hole. It is desirable that the flow rate adjusting means is disposed in the through hole.

  According to the present invention, the coolant of the gland packing is fed from the branch path to the inside of the cylinder body by having the communication path that communicates with the branch point and extends in the cylinder body to the through hole in the axial direction. Therefore, it is possible to improve the maintainability and to avoid the exposure of the liquid feeding path and improve the reliability and durability. In addition, since the liquid supply path can be connected together by assembling the cylinder, workability and handling can be improved.

In the present invention, the flow rate adjusting means is preferably a throttle or a needle valve.
According to the present invention, it is possible to simplify the configuration by reducing the flow rate adjusting means, reduce the number of parts, and improve durability and maintainability. Further, by using a needle valve as the flow rate adjusting means, it is possible to freely adjust the flow rate of the liquid sent to the gland packing, and to improve the operability and the maintenance performance of the gland packing.

  The present invention can provide a reciprocating drive pump that simplifies the liquid piping and the coolant supply path, improves the assembly, and is easy to maintain.

The longitudinal cross-sectional view of the piston pump in embodiment of this invention. II-II sectional drawing of FIG. The left view of FIG. The expanded sectional view of the flow volume adjustment means in the embodiment of the present invention. It is a longitudinal cross-sectional view which shows operation | movement of embodiment of this invention, (a) is a state which a plunger retracts, (b) is a state which a plunger advances. The expanded sectional view of the flow volume adjustment means in the 1st modification concerning the embodiment of the present invention. The longitudinal section of the piston pump in the 2nd modification concerning an embodiment of the present invention. VIII-VIII sectional drawing of FIG.

  As shown in FIG. 1, a multiple-type (triple-type) piston pump 1 that is a reciprocating drive pump according to an embodiment of the present invention uses a liquid feed pump 3 to pass liquid through an intake passage 61 a from an intake port 61. Is injected into the cylinder chamber 30 a of the cylinder body 30, and this liquid is pressurized by the plunger 20, which is a reciprocating body that reciprocates in the cylinder body 30, and is discharged from the discharge port 62.

The piston pump 1 includes a cylinder having a cylinder body 30 and a valve box 60 fixed to the tip of the cylinder body 30, and a gland packing 32 that seals a gap between the cylinder body 30 and the plunger 20. And a cooling device 50 that cools the gland packing 32. Then, the cooling device 50 supplies the branch port 51 which is a branch point where a part of the liquid supplied from the suction port 61 branches as the coolant, and the coolant branched from the branch port 51 to the gland packing 32. The cooling liquid feeding path 54 and a throttle 55 which is disposed in the cooling liquid feeding path 54 and is a flow rate adjusting means for adjusting the flow rate of the cooling liquid.
In the following description, description will be made according to the front-rear and up-down directions shown in the drawing.

  The piston pump 1 uses a liquid feed pump 3 that is a liquid supply means. The liquid feed pump 3 pumps up the liquid stored in the liquid tank 5 and feeds it to the suction port 61. A part of the liquid sucked into the piston pump 1 by this water supply pressure flows as a coolant. The coolant that has flowed through the piston pump 1 is discharged from the discharge port 57. The cooling liquid discharged from the discharge port 57 is circulated to the liquid tank 5 and used. However, since the coolant includes fine powder generated by wear of the gland packing 32, the coolant discharged from the discharge port 57 may be discarded if the liquid tank 5 does not have a filtering function.

  If the liquid level of the liquid tank 5 is sufficiently higher than the piston pump 1, the cooling water can be fed by the liquid pressure of the liquid stored in the liquid tank 5 (gravity type). Liquid supply means). In this case, the liquid feed pump 3 is unnecessary because the liquid is supplied using the potential energy due to gravity.

  The valve box 60 includes a suction port 61 for sucking liquid, a discharge port 62, suction side distribution means 41 including a valve mechanism for distributing liquid from the suction port 61 to the inside of the cylinder body 30, and the cylinder body 30. And a discharge-side distribution means 45 comprising a valve mechanism for distributing the pressurized liquid from the inside to the discharge port 62.

  In the present embodiment, a multiple-type (triple-type) piston pump 1 is described as an example of a reciprocating drive pump (see FIG. 2), but the present invention is not limited to this, and three plungers 20 are provided. Even if it is a single cylinder type reciprocating drive pump with one plunger 20, it may be applied similarly.

In the triple-type piston pump 1, three cylinder main body portions 30 are arranged in parallel in the thickness direction of the paper (see FIGS. 2 and 3). However, in the configuration relating to each cylinder (cylinder main body portion 30), The configurations of the plunger 20, the suction-side distribution means 41, the discharge-side distribution means 45, and the base portion 10 are the same.
The cylinder body 30 is a substantially hollow cylindrical member, and is fixed to the base body 10 of the piston pump 1 together with the valve box 60. The cylinder body 30 has a strength that does not yield to the pressure of the liquid pressurized by the plunger 20.

  The plunger 20 is a substantially cylindrical member, and reciprocates in the cylinder body 30 by a crank / piston mechanism. The connecting rod 12 connects the pin 11 a of the crankshaft 11 that rotates in the base portion 10 and the plunger 20. The cross head 14 slides in a column 13 provided inside the base portion 10 and separates the plunger 20 and the connecting rod 12. By providing the cross head 14, when the plunger 20 is worn by sliding with the gland packing 32, it can be easily replaced.

  A gland packing 32 and an elastic body 33 that urges the gland packing 32 rearward are disposed in front of the gland packing 32 inside the cylinder body 30. The elastic body 33 is fixed by suction side distribution means 41 that is sandwiched and fixed between the valve box 60 and the cylinder body 30. In the present embodiment, the elastic body 33 is a coil spring. The elastic body 33 urges the gland packing 32 to a ring-shaped boss portion 54 c formed by reducing the diameter of the gland packing 32 to the inner peripheral portion of the cylinder main body 30 by its elastic force. By this urging force, the gland packing 32 is compressed in the front-rear direction, and tends to expand radially outward and inward. Since the expansion of the gland packing 32 is suppressed and compressed by the cylinder body 30 and the plunger 20, the gap between the cylinder body 30 and the plunger 20 is sealed.

The valve box 60 includes a hollow 63 having a circular cross section that opens to the rear end side. The depression 63 includes a stepped portion including a depression 63a having a large cross-sectional shape and a small-diameter depression 63b formed in front of the large-diameter depression 63a.
Inside the recess 63, a valve seat 40 is disposed so as to partition a small-diameter recess 63b and a large-diameter recess 63a. The valve seat 40 is a common valve seat for the suction side distribution means 41 and the discharge side distribution means 45. The suction side distribution means 41 is disposed behind the valve seat 40, and the discharge side distribution is located in front of the valve seat 40. Means 45 are provided.
The rear of the large-diameter depression 63a is opened, the tip of the cylinder body 30 is inserted into this opening, and a cylinder chamber 30a is formed inside. The valve box 60 is provided with a liquid suction port 61, and the suction port 61 communicates with a large-diameter recess 63a.

  In the multiple piston pump 1, a plurality of cylindrical recesses 63 are also arranged in the valve box 60 corresponding to the cylinder body 30 (see FIG. 2). A through hole 64 (see FIG. 2) is provided between each large-diameter depression 63a and the large-diameter depression 63a, and communicates with each other through the suction port 61 (see FIG. 2). In addition, a through hole 65 (see FIG. 1) is provided between each small-diameter depression 63b and the small-diameter depression 63b so as to communicate with each other and to the discharge port 62.

With this configuration, on the suction side of the piston pump 1, the suction port 61 communicates with the suction-side distribution means 41 through the through hole 64 (see FIG. 2), and the liquid taken in from the suction port 61 is transferred to each cylinder body 30. Distribute to the corresponding suction side distribution means 41.
On the other hand, on the discharge side of the piston pump 1, the discharge side distribution means 45 and the discharge port 62 are communicated with each other through the through-hole 65 (see FIG. 1), and the supply is performed from the discharge side distribution means 45 corresponding to each cylinder chamber 30a. The liquid is collected and discharged from the discharge port 62.

  The suction side distribution means 41 includes a valve seat 40 common to the discharge side distribution means 45, a valve body 42 having a check valve function, a coil spring 43, and a guide 44. The discharge side distribution means 45 includes a valve seat 40 common to the suction side distribution means 41, a valve body 47 having a check valve function, a coil spring 48, and a guide 49.

  The suction side distribution means 41 is disposed behind the common valve seat 40, and the discharge side distribution means 45 is disposed in front of the common valve seat 40. The suction-side distribution means 41 and the discharge-side distribution means 45 are designed to save space by using a common valve seat 40.

  The valve seat 40 has a substantially cylindrical shape in which the central portion of the outer peripheral portion has a flange portion larger in diameter than the body portion, and the flange portion of the central portion is sandwiched between the valve box 60 and the cylinder body portion 30 and fixed. Is done.

The valve seat 40 is provided with suction passages 61a and 61a that open from the flange portion to the large-diameter recess 63a and communicate with the cylinder chamber 30a from the large-diameter recess 63a. The suction flow paths 61a and 61a are disposed at two diagonal positions (see FIG. 2).
The suction-side valve element 42 has a through hole 42a in the center, and is provided in the guide 44 so as to be slidable in the front-rear direction so that the peripheral disk portion closes the suction passages 61a, 61a. The coil spring 43 is housed along the inner peripheral surface of the guide 44 and biases the valve body 42 toward the valve seat 40.

  The valve seat 40 includes a through hole 46a along the central axis. In a state where the suction side valve body 42 is in close contact with the rear end surface of the valve seat 40 and the suction flow path 61a is closed, the through hole 42a of the valve body 42 and the through hole 46a of the valve seat 40 communicate with each other. The discharge-side valve element 47 has a rod-shaped guide part and a disk-shaped valve part, and the valve part is disposed so as to close the through hole 46 a of the valve seat 40. The guide 49 is provided inside a small-diameter recess 63b in the valve box 60, and supports the valve body 47 so as to be slidable. The coil spring 48 is disposed along the outer cylindrical surface of the guide 49 and urges the valve body 47 toward the valve seat 40.

  The cooling device 50 includes a cooling liquid supply path 54 for supplying the liquid supplied from the suction opening 61 to the gland packing 32 and a cooling liquid branched from the branch opening 51 which is a branching point of the suction flow path 61a. A throttle 55, which is disposed in the liquid feed path 54 and is a flow rate adjusting means for adjusting the flow rate of the coolant, and a connecting means 56 for connecting the throttle 55 to the piston pump so as to be detachable from the outside are provided.

  The coolant supply path 54 includes a through hole 54b that is a liquid supply path provided from the outer peripheral portion of the cylinder main body 30 toward the inner peripheral portion, a communication passage 54a that extends in the cylinder main body 30 in the axial direction, a ring And a through hole 54d that passes through the boss 54c. The aperture 55 is embedded in the opening of the through hole 54b.

  The communication path 54a is provided so as to open into the large-diameter recess 63a, and the opening of the communication path 54a that opens to the large-diameter recess 63a forms a branch port 51 that is a branch point of the suction flow path 61a. . The suction port 61, the discharge port 62, and the branch port 51 are disposed in the valve box 60 disposed at the tip of the cylinder body 30.

The through hole 54b is provided in the rear part of the cylinder body 30 and has a stepped hole having a slightly smaller diameter below, and a female screw 56a is provided at the upper end of the small diameter part below (see FIG. 4).
As shown in FIG. 4, the through hole 54 b is provided so as to open from the outer peripheral part above the rear part of the cylinder main body 30 to the ring-shaped boss part 54 c formed in the inner peripheral part of the cylinder main body 30.

  The ring-shaped boss portion 54 c forms a gap, that is, a cylindrical space 54 e between the plunger 20 and the cylinder body portion 30. The cylindrical space 54e is a gap for accumulating coolant, and as shown in FIG. 1, the front of the cylindrical space 54e communicates with the gland packing 32, and the rear of the cylindrical space 54e is sealed with the coolant packing 31. Stopped.

  The diaphragm 55 is formed inside the diaphragm member 58. The throttle member 58 is disposed in the opening of the through hole 54b that constitutes the liquid feeding path. The throttle member 58 has a substantially cylindrical shape with a step slightly narrower at the tip (see FIG. 4). An inverted L-shaped channel 58a is formed inside the throttle member 58, and a partial cross-sectional area thereof is reduced. The reduced portion of the cross-sectional area forms the diaphragm 55. A male screw 56b that is screwed into the female screw 56a is provided on the outer diameter of the distal end portion of the throttle member 58. A hexagon head is provided above the throttle member 58, and a spanner is attached to the hexagon head to attach or remove the throttle member 58. As the restriction 55, a choke restriction or an orifice restriction can be used. The flow rate of the coolant is adjusted by appropriately changing the effective sectional area of the throttle.

  The through hole 54d, the coolant packing 31 and the discharge port 57 are not provided, and the coolant can be discharged from the gap between the cylinder body 30 and the plunger 20 to the rear of the cylinder body 30. In this case, a coolant discharge port is provided at the front lower portion of the cross head shoe 15 of the base portion 10. When configured in this way, the coolant flows through the gap between the cylinder main body 30 and the plunger 20, flows from the rear of the cylinder main body 30 to the base body 10, and is discharged from the discharge port below the base body 10. .

  Next, the operation of the piston pump 1 will be described mainly with reference to FIG. The plunger 20 reciprocates in the cylinder body 30 as the crankshaft 11 rotates. As shown in FIG. 5A, when the plunger 20 moves rearward, the cylinder chamber 30a becomes negative pressure, and the liquid pressure-fed from the suction side by the liquid feed pump 3 is the valve body 42 of the suction-side distribution means 41. Is pushed against the urging force of the coil spring 43 and flows into the cylinder chamber 30a. At this time, the valve body 47 of the discharge side distribution means 45 is closed by being pressed against the valve seat 40 by the biasing force of the coil spring 48.

  At this time, a part of the liquid pumped from the suction port 61 passes through the large-diameter recess 63a, branches from the branch port 51, and circulates as the coolant to the coolant feed path 54. The flow rate of the coolant is appropriately adjusted by the throttle 55 and is supplied to the gland packing 32 through the cylindrical space (gap) 54e formed in the ring-shaped boss portion 54c, thereby cooling the gland packing 32 and the plunger 20. In addition, the sliding surfaces of the gland packing 32 and the plunger 20 are lubricated. The coolant passes through the through hole 54d and is discharged from the discharge port 57.

  As shown in FIG. 5B, when the plunger 20 moves forward, the liquid flowing into the cylinder chamber 30a is pressurized. The valve body 42 of the suction side distribution means 41 is pressed against the valve seat 40 and closed by the pressurized liquid. On the other hand, in the discharge side distribution means 45, the pressurized liquid passes through the through hole 42a of the valve body 42 of the suction side distribution means 41 and the through hole 46a in the valve seat 40, and causes the valve body 47 to become a coil spring. Push up against 48 biasing forces. Then, the valve body 47 of the discharge side distribution means 45 is opened, and the pressurized liquid is discharged from the discharge port 62 through the small diameter recess 63b.

  At this time, a part of the liquid pumped from the suction port 61 passes through the large-diameter recess 63a and branches from the branch port 51 to become a cooling liquid. That is, even when the plunger 20 moves forward (FIG. 3B), the coolant is supplied to the gland packing 32 as in the case where the plunger 20 moves backward (FIG. 3A). Therefore, a duplicate description is omitted.

(Function and effect)
In the piston pump 1 in the present embodiment, the cooling device 50 is completely housed in the piston pump 1. For this reason, it is not necessary to connect the piping to the piston pump 1 from the outside for the cooling device 50, and the piping of the cooling device 50 is not exposed to the outside of the piston pump 1. And when the piston pump 1 is incorporated in the apparatus, piping around the piston pump 1 is simplified. For this reason, in addition to improving the handling and maintenance of piping, the degree of freedom of layout of the piston pump 1 increases.

Further, the coolant supply path 54 is disassembled together with the disassembly of the piston pump 1 and is completed together with the assembly of the piston pump 1. Therefore, maintenance concerning inspection or replacement of the gland packing 32 or the plunger 20 of the piston pump 1 is very easy to perform.
Further, since the throttle 55 is disposed in the opening of the coolant supply path 54 that opens to the outer periphery of the cylinder body 30, the coolant flow rate can be easily changed, and the coolant is distributed to the gland packing 32. It can be confirmed easily.

(First modification)
Next, according to FIG. 6, a case where the flow rate adjusting means is a needle valve 80 will be described as a first modification. In addition, about the part same as the above-mentioned embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

The through hole 84 is a stepped hole having a small diameter portion at the lower portion, and a female screw 86a is provided in the vicinity of the large diameter portion opening. A step in the through hole 84 serves as a valve seat 82.
A substantially cylindrical valve body 81 having a small diameter at the tip and a conical surface at the tip is accommodated in the through hole 84. A hexagon head, which is a handle 83, and a male screw 86b screwed with the female screw 86a are provided on the upper portion of the valve body 81. The female screw 86a and the male screw 86b constitute the connecting means 86.

  The handle 83 may be any means that can rotate, and instead of a hexagon head, for example, a knob having knurled eyes, a square head, a hexagon hole, a slotted groove, a cross hole, a double chamfer, a square head, and a cylindrical direction. A groove (corresponding to the groove of a round nut) can be used.

  The valve body 81 moves up and down in the through hole 84 by a screw mechanism. When the conical surface at the tip of the valve body 81 comes into contact with the valve seat 82, the flow path is closed. By rotating the valve body and moving it up and down, the effective area changes and is adjusted to an appropriate opening.

  In the first modification, since the flow rate adjusting means is the needle valve 80, there is an advantage that the flow rate of the coolant can be freely changed for each cylinder.

(Second modification)
As shown in FIG. 7, a piston pump 100 according to a second modification example in which a cooling device is disposed outside the cylinder body 30 will be described below. In addition, about the part same as the piston pump 1 in embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

The cooling device 150 includes a coolant supply path 154 that branches the liquid supplied from the suction port 61 from the branch port 151 that is a branch point of the suction channels 61 a and 61 a and communicates to the gland packing 32. The cooling device 150 supplies the liquid supplied from the suction port 61 to the gland packing 32 from the cooling liquid supply path 154 as a cooling liquid by the liquid supply pump 3.
In the multiple piston pump 100, the coolant supply path 154 is installed for each gland packing 32 built in the cylinder body 30.

  The branch ports 151 of the respective coolant feeding paths 154 are connected to the suction ports 61 through the large-diameter recesses 63a and the through holes 64, respectively (see FIG. 8). Then, the coolant passes from the respective branch ports 151 through the restrictors 155 which are the respective flow rate adjusting means, and cools the respective plungers 20 and the gland packing 32.

  The coolant liquid supply path 154 includes a through hole 154 a that is a liquid supply path provided in the valve box 60, a pipe 154 b provided outside the cylinder main body 30, and a through hole provided in the rear part of the cylinder main body 30. 154c and a through hole 54d provided to extend downward so as to open into a cylindrical space 54e formed in a ring-shaped boss portion 54c provided to project from the inner peripheral portion of the cylinder body 30. .

  The through hole 154a penetrates from the upper surface of the valve box 60 to the cylindrical large-diameter depression 63a. The lower opening of the through hole 154a is opened so as to face the large-diameter recess 63a, and this opening forms a branch port 151 that is a branch point. The through hole 154a communicates with the cylinder chamber 30a through the suction passage 61a through the recess 63a.

  A throttle 155 that is a flow rate adjusting means is formed inside a block-shaped throttle member 158. The throttle member 158 is disposed in the upper part of the valve box 60, and is provided so that the throttle 155 communicates with the through hole 154a. The restrictor 155 is provided outside the piston pump 100, and is detachably connected by a bolt 156 that can be easily attached and detached. As the restriction 155, a choke restriction or an orifice restriction can be used. The piston pump 100 can adjust the flow rate of the coolant by appropriately changing the effective sectional area of the throttle 155.

  The diaphragm member 158 can be made of plastics, glass, steel, stainless steel, or copper alloy having high strength and weather resistance. Further, an observation window can be provided above the aperture member 158 with glass or a transparent plastic material, or the aperture member 158 can be made of a transparent material. In this case, it can be easily confirmed that the coolant is flowing into the throttle 155 through the throttle member 158.

  The installation position of the throttle member 158 may be outside the piston pump 100, but it is more preferable that the throttle member 158 is connected to the outer peripheral portion of the piston pump 100. Further, depending on the usage form of the piston pump 100, it can be appropriately changed to a position where it can be easily removed via a mounting bracket (not shown) or the like. In this case, the through hole 154a may be partially changed to external piping.

  The pipe 154b is fixed to the throttle member 158 and the through hole 154c by pipe joints 157 and 157. The pipe joint 157 provided on the throttle member 158 may be provided integrally with the throttle 155. In that case, a screw or a flange for connecting the pipe joint and the valve box 60 becomes the connecting means.

  The pipe 154b is manufactured by a hose or tube made of plastics, steel, stainless steel, copper, or copper alloy. When the pipe 154b is made of a transparent material (for example, a transparent plastics material), it can be confirmed from the outside of the pipe 154b that the coolant is supplied to the gland packing 32. When the pipe 154b is made of an opaque material, it can be confirmed that the coolant is flowing by loosening the pipe joint that fixes the pipe 154b and checking whether the coolant leaks.

The through hole 154c is opened to the ring-shaped boss portion 54c. A cylindrical space (gap) 54e to which a coolant is supplied is formed between the ring-shaped boss portion 54c and the plunger 20, and this cylindrical space (gap) is grounded along the cylindrical surface of the plunger 20. It communicates with the packing 32.
When the pipe 154 b is made of an opaque material, it can be confirmed that the coolant is supplied to the gland packing 32 by the coolant discharged from the discharge port 57.

  In this modification, the throttle member 158 is fixed to the valve box 60 by a bolt 156 that is a connecting means. However, the fixed portion is replaced by the cylinder body 30, the base body 10, or the through-hole instead of the valve box 60. It is good also as the hole 154c. When the throttle member is fixed to the through hole 154c, it can be embedded in the through hole 154c or integrated with the pipe joint. Further, the connecting means may be a female screw provided on the valve box 60 and a male screw provided on the throttle member 158 instead of the bolt 156. In this case, the throttle 155 can be integrated with the pipe joint 157, and the pipe 154b can be fixed to the pipe joint.

  It should be noted that a needle valve may be used instead of the throttle 155 that is the flow rate adjusting means. When the needle valve is used, the flow rate of the coolant can be easily adjusted by the opening degree of the needle valve. The needle valve can be integrated with a pipe joint.

(effect)
In this modification, the restrictor 155 that is a flow rate adjusting unit is exposed to the outside and can be easily removed by the connecting unit 156, so that the flow rate can be changed, the inside can be easily cleaned, or replaced. Since the flow rate adjusting means is the restriction 155, there is an effect that the coolant flows at a predetermined flow rate without being closed.
Furthermore, since the throttle 155 and the coolant feeding path 154 that are flow rate adjusting means are exposed to the outside, it can be easily confirmed that the coolant is supplied to the gland packing 32.

[Alternative]
In the above embodiment, the piston pump using the crank mechanism is described as an example of the piston pumps in which the plunger reciprocates in the cylinder. However, the cylinders are arranged in series, V shape, star shape, or the like. It doesn't matter. Further, instead of the piston pump by the crank mechanism, a swash plate type plunger pump in which the plunger reciprocates by a rotating swash plate or a plunger pump in which the plunger is directly driven by a motor by a ball screw mechanism can be applied. Further, in the above-described type of piston pump, the present invention can also be applied to a piston pump that uses a piston instead of a plunger.

1,100 piston pump (reciprocating drive pump)
3 Liquid feed pump (liquid supply means)
10 Base 20 Plunger (reciprocating body)
30 Cylinder body (cylinder)
32 Gland packing 41 Suction side distribution means 45 Discharge side distribution means 50, 150 Cooling devices 51, 151 Branch port (branch point)
54a Communication path (coolant flow path)
54b, 84, 154c Through hole (liquid feeding path)
55,155 Restriction (flow rate adjusting means)
56, 86, 156 Connecting means 54, 154 Coolant feed path 60 Valve box (cylinder)
61 Suction port 61a Suction channel 62 Discharge port 80 Needle valve (flow rate adjusting means)

Claims (5)

A cylinder having a cylinder body having a cylindrical shape, and a valve box fixed to the tip of the cylinder body,
A reciprocating body disposed in the cylinder body,
A suction port and a discharge port disposed in the cylinder;
A suction flow path communicating with the cylinder chamber from the suction port;
Liquid supply means for supplying liquid from the suction port to the cylinder chamber through the suction channel;
A gland packing that seals a gap between the cylinder body and the reciprocating body;
A cooling device for cooling the gland packing,
The cooling device includes a coolant liquid supply path that branches from a branch point of the suction flow path and communicates with the gland packing.
A reciprocating drive pump for feeding the liquid supplied to the suction port by the liquid supply means to the gland packing from the cooling liquid feeding path as a cooling liquid. The valve box includes the suction port, the discharge port, and the branch point.
The reciprocating drive pump according to claim 1. The cooling liquid supply path has an opening of a liquid supply path that opens to the outer periphery of the cylinder,
Arranging flow rate adjusting means at the opening of the liquid feeding path,
The reciprocating drive pump according to claim 1 or 2, characterized in that. The coolant flow path is
A through-hole extending from the outer periphery of the cylinder body toward the inner periphery,
A communication passage that communicates with the branch point and extends in the cylinder body portion to the through hole in the axial direction;
Arranging the flow rate adjusting means in the through hole;
The reciprocating drive pump according to claim 3.   The reciprocating drive pump according to any one of claims 1 to 4, wherein the flow rate adjusting means is a throttle or a needle valve.

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