JP2015031262A - Engine driven work machine - Google Patents

Abstract

An engine-driven work machine capable of satisfactorily evaporating raw water with engine waste heat is provided.
An engine-driven work machine 10 includes a water generating device 20 that evaporates raw water 29 with waste heat of an engine 12 and condenses the evaporated water vapor to generate purified water 69. The water generator 20 includes an evaporator 35 that evaporates the raw water 29 with the waste heat of the exhaust gas guided to the heating unit 53. The heating unit 53 includes a gas intake unit 66 that takes in the exhaust gas from the exhaust pipe 27, and a gas discharge unit 67 that discharges the exhaust gas taken in from the gas intake unit 66 to the outside 68 of the evaporator 35. The heating body 65 is inclined downwardly from the gas intake portion 66 toward the gas discharge portion 67.
[Selection] Figure 5

Description

  The present invention relates to an engine-driven work machine including a water generating device that evaporates raw water with engine waste heat and condenses the evaporated water vapor to generate purified water.

  As an engine-driven work machine, water (raw water) such as rivers is taken into the water pump, a part of the taken raw water is branched, the branched raw water is evaporated by the waste heat of the engine, and the raw water is branched from the evaporated steam It is known that the water is condensed to produce purified water.

  According to the engine-driven working machine, while driving the water pump, a part of the raw water taken into the water pump is guided to the raw water branch pipe, and the guided raw water is guided to the engine exhaust pipe through the raw water branch pipe. The guided raw water is evaporated by the waste heat of the exhaust pipe (that is, the waste heat of the engine), and the evaporated water vapor is raised along the communication pipe to the raw water branch pipe. Purified water is generated by condensing the raised water vapor with the raw water in the raw water branch pipe. The produced | generated purified water is used as drinking water, for example (for example, refer patent document 1).

JP 2012-24699 A

Here, the engine-driven working machine of Patent Document 1 preferably suppresses the volume of raw water supplied to the evaporation region in order to shorten the time for evaporating the raw water with the waste heat of the engine. Furthermore, in order to shorten the evaporation time of raw water, it is preferable to immerse the entire exhaust pipe in a small volume of raw water. Therefore, the exhaust pipe is disposed horizontally in the evaporation region.
Therefore, water vapor bubbles vaporized below the exhaust pipe are blocked by the exhaust pipe and are difficult to move upward. For this reason, it is difficult to evaporate raw water well with waste heat of exhaust gas flowing through the exhaust pipe (that is, waste heat of the engine), and there remains room for improvement from this viewpoint.

  This invention makes it a subject to provide the engine drive working machine which can evaporate raw | natural water favorably with the waste heat of an engine.

  The invention according to claim 1 is directed to an engine-driven working machine including a water generating device that evaporates raw water with waste heat of the engine during driving of the engine and condenses the evaporated water vapor to generate purified water. The generating apparatus includes a heating unit that guides the exhaust gas of the engine to the inside, and an evaporator that evaporates the raw water with the waste heat of the exhaust gas guided to the heating unit to form water vapor, and A portion communicating with the exhaust pipe of the engine, a gas intake portion for taking in the exhaust gas from the exhaust pipe, and a gas discharge portion for discharging the exhaust gas taken in from the gas intake portion to the outside of the evaporator; , And is inclined downwardly from the gas intake portion toward the gas discharge portion.

  The invention according to claim 2 is characterized in that the gas discharge portion is formed in a substantially rectangular cross section.

  According to a third aspect of the present invention, in the heating unit, the upstream portion of the gas discharge portion is bent in an upward crank shape toward the gas intake portion, and protrudes upward from the upstream portion. A step portion is provided.

Here, the exhaust gas led to the gas discharge unit may be cooled by being exposed to the atmosphere, and condensed water may be generated in the gas discharge unit. In addition, rainwater or the like may enter the gas discharge part from the outside of the evaporator. It is conceivable that condensed water generated in the gas discharge part, rain water entering the gas discharge part, etc. enter the heating part.
Therefore, in claim 3, the upstream portion of the gas discharge portion is bent in an upward crank shape, and a step portion protruding upward is formed at this portion.

In the invention which concerns on Claim 1, the heating part of the evaporator was made to incline in the downward slope toward the gas discharge part from the gas intake part. Therefore, a gas intake part can be arrange | positioned in a position higher than a gas discharge part. The gas intake part is a part where the exhaust gas is taken from the exhaust pipe, and the temperature due to the waste heat of the exhaust gas is higher than the other part.
Therefore, a relatively large amount of bubbles (water vapor) is generated around the gas intake portion, and the generated bubbles move upward (float). By moving a large amount of bubbles upward, the raw water at the lower part of the heating part rises obliquely toward the gas intake part along the lower part.

  The raw water rising obliquely is heated by the waste heat of the heating unit while moving, and the temperature rises. When the temperature of the raw water rises, convection (natural body flow) occurs in the raw water in the evaporator, and the same effect as a so-called counterflow heat exchanger can be obtained.

  Thus, raw water can be suitably heated in the whole area of the lower part of a heating part by heating raw water in a heating part, moving raw water along the lower part of a heating part. Thereby, the heat exchange between the waste heat of a heating part and raw | natural water can be performed efficiently.

In other words, by generating convection (natural body flow) in the raw water in the evaporator, it is possible to smoothly move the bubbles vaporized below the heating unit (lower part) upward. Accordingly, the raw water can be favorably evaporated by the waste heat of the exhaust gas flowing through the heating unit (that is, the waste heat of the engine).
Water vapor can be secured by evaporating raw water well. Purified water can be suitably generated by condensing the water vapor.

By the way, when draining raw water from the evaporator, the raw water may remain in the upper part of the heating unit. In addition, when the water level of the raw water stored in the evaporator decreases below the heating unit, the raw water may remain on the upper part of the heating unit.
When raw water remains on the upper part of the heating unit, the upper part of the heating unit may be corroded by the remaining raw water.

Here, the heating part of the evaporator is inclined downwardly from the gas intake part toward the gas discharge part. Therefore, when draining raw water or when the surface of the raw water decreases to below the heating unit, the raw water at the upper part of the heating unit can be guided obliquely downward along the upper part.
Thereby, it is possible to prevent raw water from remaining in the upper part of the heating unit, and to prevent the upper part of the heating unit from being corroded by raw water.

  In the invention which concerns on Claim 2, the gas discharge part was formed in cross-sectional substantially rectangular shape. Therefore, compared with the case where the gas discharge part is formed in another shape such as a circular cross section or an elliptical cross section, it is possible to suitably adjust the cross sectional area of the gas discharge part while suppressing the height of the gas discharge part to be small.

Therefore, the gas discharge part can be lowered toward the lower part of the heating part. Thereby, a heating part can be easily made to incline in a downward slope toward a gas discharge part from a gas intake part.
Furthermore, since the cross-sectional area of the gas discharge part can be adjusted suitably, the exhaust pressure of the exhaust gas led to the heating part (back pressure, the pressure of the exhaust gas in the heating part) can be adjusted well, and the exhaust gas in the heating part can be adjusted. Waste heat can be suitably transmitted.

In the invention which concerns on Claim 3, the level | step-difference part was formed in the site | part upstream of a gas discharge part among heating parts. Therefore, the stepped portion can prevent the condensed water generated from the exhaust gas in the gas discharge portion, the rainwater entering from the gas discharge portion, and the like from entering the heating portion.
As a result, it is possible to prevent the condensed water generated in the gas discharge part, the rainwater entering from the gas discharge part and the like from entering the combustion chamber of the engine.

It is a perspective view which shows the state which looked at the engine drive working machine which concerns on this invention from the front side. It is a perspective view which shows the state which looked at the engine drive work machine of FIG. 1 from the back side. It is a perspective view which shows the water production | generation part of FIG. It is a perspective view which shows the state which looked at the water production | generation part of FIG. 3 from the front side. FIG. 5 is a sectional view taken along line 5-5 of FIG. FIG. 6 is a sectional view taken along line 6-6 of FIG. FIG. 7 is a cross-sectional view taken along line 7-7 in FIG. 6. FIG. 8 is an enlarged view of 8 parts in FIG. 3. FIG. 6 is an enlarged view of 9 parts in FIG. 5. It is a figure explaining the example which evaporates raw | natural water with the heating part which concerns on this invention.

  The best mode for carrying out the present invention will be described below with reference to the accompanying drawings. In the drawing, the front, rear, left side and right side are indicated by “Fr”, “Rr”, “L” and “R”.

An engine-driven work machine 10 according to an embodiment will be described.
As shown in FIGS. 1 and 2, the engine-driven work machine 10 is integrated with a frame 11 that forms an outer frame of the engine-driven work machine 10, an engine 12 that is provided at the lower left front of the frame 11, and the engine 12. An operation provided in front of a generator 13 provided in the water, a water generating device 20 provided adjacent to the generator 13 and the engine 12, and a fuel tank 22 of the engine 12 and a raw water tank 41 of the water generating device 20. An engine driving generator including a panel 15.

The frame 11 includes a base 17 that supports the water purification tank 33 of the engine 12, the generator 13, and the water generator 20, a left frame 18 that is bent upward from the left end of the base 17, and a right end of the base 17. And a right frame 19 bent upward.
The engine-driven working machine 10 can be transported (carried) by manually grasping the gripping part 18 a of the left frame 18 and the gripping part 19 a of the right frame 19 and lifting the engine-driven working machine 10.

The engine 12 is supported by the front left lower portion 17 a of the base 17, and the right end portion of the crankshaft is coaxially connected to the drive shaft of the generator 13. Further, the left end portion of the crankshaft is connected to the cooling fan 23, and the cooling fan 23 is connected to the recoil starter 24.
Further, the exhaust port 28 (see FIG. 5) of the cylinder head (engine head) 25 is communicated with the evaporator 35 of the water generating device 20 via the exhaust pipe 27 (see FIG. 4). Therefore, when the engine 12 is driven, the exhaust gas is guided to the evaporator 35 of the water generator 20 through the exhaust port 28 and the exhaust pipe 27.

The cooling fan 23 is a device that cools the cylinder block and the cylinder head 25 by sending cooling air to the cylinder block and the cylinder head 25 of the engine 12. The tip of the cylinder head 25 is covered with a head cover 26.
The recoil starter 24 is a device that starts the engine 12.

  The generator 13 includes a drive shaft communicating with the crankshaft of the engine 12 and a rotor provided on the drive shaft. The rotor rotates by rotating the drive shaft with the crankshaft, and electric power is generated by rotating the rotor.

The water generator 20 is disposed in a space formed by the generator 13, the cylinder block, the cylinder head 25, and the head cover 26.
The water generation device 20 is generated by a raw water supply unit 31 that supplies raw water 29 (see FIG. 5), a water generation unit 32 that generates purified water from the raw water 29 supplied from the raw water supply unit 31, and a water generation unit 32. A purified water tank 33 for storing the purified water.
The water generator 32 is supported on the generator 13 side via a first bracket 34a and a second bracket 34b.

As shown in FIGS. 3 and 4, the water generator 32 includes an evaporator 35 that evaporates the raw water 29 supplied from the raw water supply means 31, a bottom cover 36 that covers the lower portion of the evaporator 35, and the evaporator 35. A coagulator 38 that condenses the evaporated water vapor and a separator 39 that collects (collects) purified water (distilled water) 69 generated by the coagulator 38 are included (provided).
That is, the water generator 20 has a function of generating purified water by condensing the vapor evaporated by the evaporator 35 by the aggregator 38.

  The raw water supply means 31 is provided above the water generator 32 and stores a raw water tank 41 for storing raw water 29, a raw water supply passage 42 for guiding (supplying) the raw water 29 stored in the raw water tank 41 to the evaporator 35, and An air vent passage 45 that communicates the internal space 43 (see FIG. 5) of the evaporator 35 and the internal space of the raw water tank 41 is provided.

As shown in FIGS. 4 and 5, the evaporator 35 includes an evaporation container 51 having an outer peripheral wall 52 formed in a substantially rectangular frame shape, and a heating unit (heat exchange unit) 53 provided in the evaporation container 51. It has.
In the evaporation container 51, the bottom cover 36 is attached to the lower part 51 a, so that the lower part 51 a is closed by the bottom cover 36.
A raw water storage tank 48 is formed by the evaporation container 51 and the bottom cover 36. The raw water 29 supplied from the raw water tank 41 is stored in the raw water storage tank 48.

The outer peripheral wall 52 of the evaporation container 51 is formed in a substantially rectangular frame shape by the first wall portion 55, the second wall portion 56, the third wall portion 57 (see FIG. 3), and the fourth wall portion 58 (see FIG. 3). Has been.
The first wall portion 55 is integrally provided with a gas intake portion 66 of the heating portion 53. An inlet 66 a of the gas intake portion 66 is communicated with the exhaust port 28 of the engine 12 through the exhaust pipe 27. Further, the outlet 66b of the gas intake part 66 is communicated with the heating inlet 65a of the heating part 53 (heating body 65).

  A raw water intake portion 63 is provided on the first wall portion 55, and an air vent portion 64 is provided on the second wall portion 56. An outlet 63 a of the raw water intake portion 63 is communicated with the inside of the evaporation container 51, and an outlet 42 a of the raw water supply path 42 is communicated with an inlet 63 b of the raw water intake portion 63. The air vent 64 communicates with the inside of the evaporation container 51, and the air vent path 45 communicates with the air vent 64.

  A gas discharge part 67 of the heating part 53 is provided integrally with the third wall part 57. An inlet 67 a of the gas discharge unit 67 is communicated with a heating outlet 65 b of the heating unit 53 (heating body 65), and an outlet 67 b of the gas discharge unit 67 is opened to the outside 68 of the evaporator 35.

The heating unit 53 is a heat exchanger that guides exhaust gas into the evaporator 35.
The heating unit 53 includes a heating main body 65 accommodated in the evaporator 35, a gas intake unit 66 communicated with the heating inlet 65 a of the heating main body 65, and a gas discharge communicated with the heating outlet 65 b of the heating main body 65. Part 67.

The heating main body 65 has a heating inlet 65 a communicating with the gas intake part 66 and a heating outlet 65 b communicating with the gas discharge part 67.
The gas intake portion 66 is a flow path that communicates with the exhaust pipe 27 of the engine 12 and takes in the exhaust gas from the exhaust pipe 27.
The gas discharge part 67 is a flow path for discharging the exhaust gas taken into the heating main body 65 from the gas intake part 66 to the outside 68 of the evaporator 35.

The exhaust gas of the engine 12 is guided to the heating inlet 65a of the heating main body 65 through the exhaust pipe 27 and the gas intake portion 66, and is guided to the heating main body 65 through the heating inlet 65a.
The exhaust gas guided to the heating body 65 is guided to the gas discharge portion 67 through the heating outlet 65b of the heating body 65. The exhaust gas guided to the gas discharge unit 67 is discharged from the outlet 67 b of the gas discharge unit 67 to the outside 68 of the evaporator 35.

By introducing the exhaust gas of the engine 12 to the heating unit 53, the heating unit 53 is heated by the waste heat of the exhaust gas (waste heat of the engine 12). By heating the heating unit 53, the raw water 29 stored in the raw water storage tank 48 can be evaporated by the heating unit 53.
That is, the evaporator 35 has a function of evaporating the raw water 29 stored in the evaporation container 51 using the waste heat of the engine 12.
The heating unit 53 will be described in detail with reference to FIGS.

  The aggregator 38 is provided on the agglomeration container 75 having a top portion 76 that covers the top of the evaporation vessel 51, a plurality of cooling fins 81 provided on the outer surface (upper surface) 76a of the top portion 76, and the inner surface (lower surface) 76b of the top portion 76. The plurality of right condensing fins 82 and the plurality of left condensing fins 84 are included.

The aggregation container 75 has a top portion 76 that covers the upper side of the evaporation container 51, and an outer peripheral wall 77 provided on the outer peripheral edge of the top portion 76.
A plurality of cooling fins 81 are provided on the outer surface 76 a of the top portion 76 and a part of the outer peripheral wall 77. Therefore, the aggregator 38 has a large area facing the atmosphere (external 68). Thereby, heat exchange is efficiently performed by the plurality of cooling fins 81, and the aggregator 38 can be kept in a suitable cooling state.

Further, among the inner surface 76b of the top portion 76, a plurality of right condensing fins 82 are provided in the right condensing portion 76d above the evaporating vessel 51 (third wall portion 57), and above the evaporating vessel 51 (first wall portion 55). A plurality of left condensing fins 84 are provided in the left condensing portion 76e.
Therefore, the plurality of right condensing fins 82 and the plurality of left condensing fins 84 are kept in a suitable cooling state by the plurality of cooling fins 81.

As a result, the water vapor introduced from the evaporator 35 to the aggregator 38 is condensed by coming into contact with the plurality of right condensing fins 82 and the plurality of left condensing fins 84 and adheres to the respective condensing fins 82 and 84 as purified water 69. .
That is, the aggregator 38 is provided above the evaporator 35 and has a function of generating purified water by condensing the water vapor evaporated by the evaporator 35 at the right condensing part 76d and the left condensing part 76e.

The purified water generated by the aggregator 38 is collected by the separator 39.
The separator 39 is interposed between the evaporator 35 and the aggregator 38, and an opening 88 is formed at the center 39a. By forming the opening 88 in the separator 39, the water vapor evaporated by the evaporator 35 is guided to the aggregator 38 through the opening 88.

On the other hand, by interposing the separator 39 between the evaporator 35 and the aggregator 38, the purified water 69 dripped from the aggregator 38 (the plurality of right condensing fins 82 and the plurality of left condensing fins 84) is collected by the separator 39.
The purified water 69 collected by the separator 39 is stored in the purified water tank 33 (see FIG. 2) via the purified water outlet 89 and the purified water outlet 91 (see FIG. 4). The purified water 69 stored in the purified water tank 33 is used as drinking water, for example.

Next, the heating unit 53 will be described in detail with reference to FIGS.
As shown in FIGS. 5 and 6, in the heating unit 53, the heating main body 65 is inclined at a downward gradient of the inclination angle θ from the gas intake unit 66 toward the gas discharge unit 67. That is, the lower heating portion 65 c and the upper heating portion 65 d of the heating main body 65 are inclined downwardly at an inclination angle θ from the gas intake portion 66 toward the gas discharge portion 67.

  A plurality of upper heating fins 71 are provided on the heating upper portion 65 d of the heating body 65. The plurality of upper heating fins 71 project upward from the heating upper portion 65 d and are provided along the inclination direction of the heating main body 65. Further, the plurality of upper heating fins 71 are formed at a predetermined interval in a direction (arrow A direction) orthogonal to the inclination direction.

  A plurality of lower heating fins 72 are provided on the heating lower portion 65 c of the heating main body 65, similarly to the heating upper portion 65 d of the heating main body 65. The plurality of lower heating fins 72 project downward from the heating lower portion 65 c and are provided along the inclination direction of the heating main body 65. Further, the plurality of lower heating fins 72 are formed at a predetermined interval in a direction (arrow A direction) orthogonal to the inclination direction.

  A plurality of upper heating fins 71 are provided on the heating upper portion 65 d of the heating main body 65, and a plurality of lower heating fins 72 are provided on the heating lower portion 65 c of the heating main body 65, whereby exhaust heat of exhaust gas led to the heating main body 65 is provided. And heat exchange with the raw | natural water 29 of the raw | natural water storage tank 48 can be performed efficiently.

As shown in FIGS. 5 and 7, the heating main body 65 is inclined downward, and the gas intake part 66 is disposed at a position higher than the gas discharge part 67. Further, the gas intake part 66 is a part where exhaust gas is taken in from the exhaust pipe 27.
The exhaust gas is taken into the gas intake part 66 from the exhaust pipe 27, so that the temperature due to the waste heat of the exhaust gas is higher than that of other parts.

Therefore, the raw water 29 in the raw water storage tank 48 is efficiently heated around the gas intake portion 66 in the heating main body 65 (that is, in the vicinity of the heating inlet 65a of the heating main body 65).
By heating the raw water 29, a relatively large amount of bubbles (water vapor) is generated in the vicinity of the heating inlet 65a of the heating body 65. A large amount of generated bubbles move upward (float) as indicated by arrow B.

As a large amount of bubbles move upward, the raw water 29 on the heating lower part 65c side of the heating body 65 rises obliquely as indicated by an arrow C along the heating lower part 65c toward the gas intake part 66.
Here, a plurality of lower heating fins 72 are provided along the inclination direction of the heating main body 65. Therefore, there is no possibility that the plurality of lower heating fins 72 block the flow of the raw water 29.
As a result, the bubbles vaporized on the lower side of the heating main body 65 (heating lower portion 65c) smoothly move obliquely upward toward the gas intake portion 66 side.

By the way, when draining (draining) the raw water 29 from the raw water storage tank 48, the raw water 29 may remain (remain) in the heating upper portion 65 d of the heating main body 65. In addition, when the water surface 29 a of the raw water 29 stored in the evaporator 35 decreases below the heating main body 65 (heating upper portion 65 d), the raw water 29 may remain in the heating upper portion 65 d of the heating main body 65.
When the raw water 29 remains in the heating upper portion 65 d of the heating main body 65, it is considered that the heating upper portion 65 d of the heating main body 65 is corroded by the remaining raw water 29.

  Here, the heating upper portion 65 d of the heating main body 65 is inclined downward from the gas intake portion 66 toward the gas discharge portion 67. Therefore, when draining the raw water 29, or when the water surface 29a of the raw water 29 decreases to below the heating upper part 65d, the raw water 29 in the heating upper part 65d of the heating body 65 is obliquely downward along the heating upper part 65d. Can be guided as follows.

Here, a plurality of upper heating fins 71 are provided along the inclination direction of the heating main body 65. Therefore, there is no possibility that the plurality of upper heating fins 71 block the flow of the raw water 29.
Thereby, it is possible to prevent the raw water 29 from remaining in the heating upper portion 65 d of the heating main body 65, and to prevent the heating upper portion 65 d from being corroded by the raw water 29.

As shown in FIGS. 6 and 8, the gas discharge part 67 is formed in a substantially rectangular cross section at an upper part 93, a lower part 94, a front side part 95 and a rear side part 96.
A relatively large cross-sectional area can be secured by forming the gas discharge portion 67 in a substantially rectangular cross section. Therefore, the cross-sectional area of the gas discharge part 67 can be suitably adjusted in a state where the height dimension H of the gas discharge part 67 is kept relatively small.

  Specifically, as compared with the case where the gas discharge part 67 is formed in another shape such as a circular cross-section or an elliptical cross-section, the cross-sectional area of the gas discharge part 67 is suppressed while keeping the height dimension H of the gas discharge part 67 small. Can be adjusted. Therefore, the upper part 93 of the gas discharge part 67 can be lowered toward the heating lower part 65 c of the heating body 65.

Thereby, the heating main body 65 of the heating part 53 can be easily inclined toward the downward inclination of the inclination angle θ (see FIG. 5) from the gas intake part 66 toward the gas discharge part 67.
Furthermore, since the cross-sectional area of the gas discharge part 67 can be adjusted suitably, the exhaust pressure of the exhaust gas led to the heating part 53 (back pressure, the pressure of the exhaust gas in the heating part) can be adjusted well. The waste heat of exhaust gas can be transmitted suitably.

As shown in FIG. 9, the upper dimension 93 of the gas discharge part 67 is formed below the heating upper part 65 d of the heating body 65 by suppressing the height dimension H of the gas discharge part 67 to be small. Furthermore, the lower part 94 of the gas discharge part 67 is formed below the heating lower part 65 c of the heating body 65.
In the heating unit 53, an upstream portion (hereinafter referred to as an upstream portion) 98 of the gas discharge portion 67 is bent in an upward crank shape toward the gas intake portion 66 (see FIG. 5). The upstream portion 98 is formed by an inlet 67 a of the gas discharge part 67, a heating outlet 65 b of the heating main body 65, and the like.

Since the lower part 94 of the gas discharge part 67 is formed below the heating lower part 65c of the heating body 65, a step part 99 (also FIG. 6) is formed in the upstream portion 98 (specifically, the heating outlet 65b of the heating body 65). Reference) is formed.
The step part 99 is erected upward from the lower part 94 of the gas discharge part 67 to the heating lower part 65c of the heating body 65.

Here, the exhaust gas led to the gas discharge unit 67 may be cooled by being exposed to the atmosphere, and condensed water 101 may be generated in the gas discharge unit 67. In addition, rainwater or the like may enter the outlet 67 b of the gas discharge unit 67 from the outside 68 of the evaporator 35.
It is conceivable that the condensed water 101 generated in the gas discharge unit 67, rainwater that has entered the outlet 67b of the gas discharge unit 67, or the like enters the heating unit 53 (particularly, the heating main body 65).

Therefore, a stepped portion 99 is formed in the upstream portion 98 (specifically, the heating outlet 65b). Therefore, the condensed water 101 generated from the exhaust gas in the gas discharge unit 67, rainwater that has entered the gas discharge unit 67 (exit 67b) from the outside 68 of the evaporator 35 enters the heating unit 53 (heating body 65). This can be prevented by the step portion 99.
Thereby, it is possible to prevent the condensed water 101 generated in the gas discharge part 67 and rainwater entering the gas discharge part 67 (exit 67b) from entering the combustion chamber of the engine 12 (see FIG. 5).

Next, an example in which the raw water 29 is evaporated by the heating unit 53 will be described with reference to FIG.
As shown in FIG. 10A, the exhaust gas of the engine 12 is guided to the heating unit 53 through the exhaust pipe 27 and the gas intake unit 66 as indicated by an arrow E. The exhaust gas guided to the heating unit 53 is discharged as indicated by an arrow F to the outside 68 of the evaporator 35 through the gas discharge unit 67.

By introducing the exhaust gas of the engine 12 to the heating unit 53, the heating unit 53 (particularly the heating main body 65) is heated by the waste heat of the exhaust gas (waste heat of the engine 12). When the heating main body 65 is heated, heat exchange is performed with the raw water 29 stored in the raw water storage tank 48, and the raw water 29 is evaporated to generate water vapor.
The water vapor of the raw water 29 is guided through the opening 88 of the separator 39 to the right condensing fin 82 in the right condensing portion 76d and the left condensing fin 84 in the left condensing portion 76e as indicated by an arrow G.

  The right condensing fins 82 and the left condensing fins 84 are kept in a suitable cooling state by the cooling fins 81. Therefore, the water vapor guided to the right condensation fins 82 and the left condensation fins 84 is cooled by the respective condensation fins 82 and 84, and the purified water 69 is generated in a state of adhering to the right condensation fins 82 and the left condensation fins 84.

By the way, the heating part 53 has the heating main body 65 inclined downwardly from the gas intake part 66 toward the gas discharge part 67. The gas intake part 66 is a part where the exhaust gas is taken in from the exhaust pipe 27, and the temperature due to the waste heat of the exhaust gas is higher than the other parts.
As the temperature of the gas intake section 66 increases, the raw water 29 in the raw water storage tank 48 is efficiently heated around the gas intake section 66 of the heating main body 65 (that is, in the vicinity of the heating inlet 65a of the heating main body 65).

By heating the raw water 29, a relatively large amount of bubbles (water vapor) is generated in the vicinity of the heating inlet 65a of the heating body 65. Bubbles generated in a large amount move upward (floating) as indicated by an arrow H.
As a large amount of bubbles move upward, the raw water 29 on the heating lower portion 65c side of the heating main body 65 rises obliquely as indicated by an arrow I along the heating lower portion 65c toward the gas intake portion 66.
Thereby, the bubble vaporized by the lower side of the heating main body 65 (heating lower part 65c) can be smoothly moved diagonally upward toward the gas intake part 66 side.

  As shown in FIG. 10B, the raw water 29 rising obliquely is heated by the waste heat of the heating main body 65 while moving, and the temperature rises. When the temperature of the raw water 29 rises, convection (natural body flow) is generated in the raw water 29 in the evaporator 35, and the same effect as a so-called counterflow heat exchanger is obtained.

  In this way, by heating the raw water 29 with the heating main body 65 while moving the raw water 29 along the heating lower part 65 c of the heating main body 65, the raw water 29 can be suitably heated in the entire area E of the heating main body 65. Thereby, the heat exchange between the waste heat of the heating main body 65 and the raw water 29 can be efficiently performed.

In other words, by generating convection (natural body flow) in the raw water 29 in the evaporator 35, the bubbles vaporized below the heating body 65 (the heating lower part 65c) can be smoothly moved upward. Therefore, the raw water 29 can be favorably evaporated by the waste heat of the exhaust gas flowing through the heating main body 65 (that is, the waste heat of the engine 12).
Water vapor can be secured by evaporating the raw water 29 well. By condensing the water vapor with the aggregator 38 (see FIG. 10A), the purified water 69 can be suitably generated.

The engine-driven work machine according to the present invention is not limited to the above-described embodiments, and can be changed or improved as appropriate.
For example, in the above-described embodiment, an example in which the engine-driven work machine 10 is applied to a power generator has been described. It is also possible to apply to other working machines.

  In addition, the shapes and configurations of the engine-driven work machine, the engine, the water generation device, the exhaust pipe, the evaporator, the heating unit, the gas intake unit, the gas discharge unit, the upstream portion, and the stepped portion shown in the above embodiment are illustrated. It is not limited to a thing, It can change suitably.

  INDUSTRIAL APPLICABILITY The present invention is suitable for application to an engine-driven working machine including a water generation device that evaporates raw water with engine waste heat and condenses the evaporated water vapor to generate purified water.

  DESCRIPTION OF SYMBOLS 10 ... Engine drive work machine, 12 ... Engine, 20 ... Water production | generation apparatus, 27 ... Exhaust pipe, 29 ... Raw water, 35 ... Evaporator, 43 ... Internal space of evaporator (inside of evaporator), 53 ... Heating part, 66 ... Gas intake part, 67 ... Gas discharge part, 68 ... Outside of the evaporator, 69 ... Clean water, 98 ... Upstream part (upstream part of the gas discharge part), 99 ... Step part.

Claims (3)

In an engine-driven working machine equipped with a water generating device that evaporates raw water with waste heat of the engine during driving of the engine and condenses the evaporated water vapor to generate purified water,
The water generator is
A heating unit that guides the exhaust gas of the engine to the inside; and an evaporator that evaporates the raw water with waste heat of the exhaust gas guided to the heating unit to form water vapor,
The heating unit is
A gas intake portion that is in communication with an exhaust pipe of the engine and takes in the exhaust gas from the exhaust pipe;
A gas discharge part for discharging the exhaust gas taken in from the gas intake part to the outside of the evaporator,
An engine-driven work machine, wherein the engine-driven work machine is inclined downwardly from the gas intake unit toward the gas discharge unit.   The engine-driven work machine according to claim 1, wherein the gas discharge part is formed in a substantially rectangular shape in cross section. The heating unit is
The upstream portion of the gas discharge portion is bent in an upward crank shape toward the gas intake portion, and a step portion protruding upward is provided at the upstream portion. The engine-driven work machine according to claim 1 or 2.

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